TWI815074B - Fan motor - Google Patents

Abstract

The present disclosure relates to a fan motor, including a rotating shaft provided with a first support portion and a second support portion spaced apart from each other in an axial direction, and a permanent magnet mounting portion disposed between the first support portion and the second support portion; an impeller provided at one end portion of the rotating shaft; an air bearing disposed adjacent to the impeller, and lubricated with air with an air gap to the first support portion to rotatably support the first support portion; a permanent magnet mounted on the permanent magnet mounting portion; and a ball bearing provided at the other end portion of the rotating shaft at a side opposite to the first support portion with the permanent magnet interposed therebetween to rotatably support the second support portion, thereby allowing downsizing and weight reduction as well as rotating at high speed.

Description

fan motor

The present invention relates to a fan motor suitable for high-speed rotation of a fan.

The motor may be incorporated into household appliances such as vacuum cleaners or hair dryers.

A vacuum cleaner or hair dryer can use a motor as a power source to create rotational force.

For example, the motor may be coupled to a fan. The fan can rotate by receiving power from the motor to generate airflow.

A vacuum cleaner or hair dryer operates when the user lifts it by hand.

In order to increase portability and convenience for the user, it is necessary to reduce the size and weight of the vacuum cleaner or hair dryer.

For this reason, it is necessary to reduce the size and weight of the motor while increasing the output of the motor. In addition, high-speed rotation of the motor is necessary.

US Patent Publication No. 2010/0215491 A1 (published on August 26, 2010, hereinafter referred to as Patent Document 1) discloses a rotor assembly.

The rotor assembly includes a rotating shaft member. The impeller, rotor core and bearing frame are installed on the rotating shaft. The bearing frame is arranged between the impeller and the rotor core.

The bearing frame consists of two ball bearings, springs and sleeves.

The bearing frame supports the rotating shaft with two ball bearings.

The bearing frame places a spring between two ball bearings, and the spring applies preload to each of the two ball bearings, ensuring the life of the ball bearings.

The bearing frame can extend the life of the ball bearings by aligning the sleeve with the outer ring of the ball bearing and housing the two ball bearings inside the sleeve.

However, according to Patent Document 1, when two ball bearings are applied to a fan motor, it is not Helps reduce the size and weight of the fan motor.

For example, in order to reduce the size and weight of a fan motor, the size of the ball bearing should be smaller, but the ball bearing has a structure in which a plurality of balls are in rolling contact between the outer ring and the inner ring, so the smaller the size of the ball bearing, the more disadvantageous it is In terms of load-bearing, the larger the size of the ball bearing, the less suitable it is for high speeds.

In more detail, the smaller the size of the ball bearing, the smaller the diameter of the rotating shaft. However, if the diameter of the rotating shaft is too small, the problem of bending of the rotating shaft may occur.

In particular, between the two ball bearings, the support portion of the rotating shaft on which the ball bearing adjacent to the impeller is installed will cause a more serious bending problem due to the unbalanced load of the impeller.

In addition, if the diameter of the rotating shaft is too small, the limit speed allowed by the rotating shaft will be reduced, and it will become more dangerous as the operating speed of the fan motor increases.

On the other hand, in order to allow the rotating shaft to withstand high-speed rotation, the larger the diameter of the rotating shaft, the larger the diameter of the ball bearing. In this case, there is a problem that the life of the ball bearing is shortened.

U.S. Patent Publication No. 2018/0363669 A1 (published on December 20, 2018, hereinafter referred to as Patent Document 2) discloses an electric machine.

The electrical machine includes a rotor assembly. The rotor assembly includes a first ball bearing and a second ball bearing. The first ball bearing and the second ball bearing are installed on both sides of the rotating shaft member, and there is a rotor core permanent magnet between them.

O-rings can be provided on the outer circumferential surface of the ball bearing to extend the life of the ball bearing.

However, when the two ball bearings of Patent Document 2 are applied to a fan motor, it is not conducive to reducing the size and weight of the fan motor. Since its detailed description is the same as or similar to Patent Document 1, its repeated description will be omitted.

On the other hand, the motor may include a bearing that supports the weight of the rotating shaft and a load that is applied to the rotating shaft when fixing the rotating shaft at a predetermined position.

However, when the motor is used in a vacuum cleaner, dust moved through the airflow generated by the characteristics of the traveling environment may enter the operating area of the bearing, thereby damaging the bearing, and damage to the bearing will reduce the reliability of the motor operation. sex.

In order to solve this problem, in the case of rolling bearings such as ball bearings or roller bearings, a dust cover is provided. The dust cover blocks the internal space of the ball or roller by shielding it. Dust from the external environment.

On the other hand, the air bearing has a more advantageous aspect for the rotating shaft of a motor rotating at high speed, so various attempts have been made to apply it to the rotating shaft of an ultra-high-speed motor used in a vacuum cleaner.

The air bearing has a structure in which the operating area of the bearing is open to allow air to enter and exit through a gap formed between the rotating shaft member and the bearing for the bearing to operate.

The air bearing is configured to support the rotating shaft through air flowing through a gap formed between the rotating shaft and the bearing.

However, due to the characteristics of the above-mentioned operating mechanism of the bearing, the air bearing cannot use a dust cover structure to completely seal the operating area, thus causing a problem that it is difficult to completely prevent foreign matter such as dust from entering the operating area of the bearing.

A first aspect of the present invention aims to provide a fan motor that can reduce size and weight and can rotate at a high speed of more than 100,000 revolutions per minute.

A second aspect of the present invention aims to provide a fan motor that can extend the bearing life even if the diameter of the rotating shaft is increased.

A third aspect of the present invention aims to provide a fan motor that can increase the allowable limit speed even during high-speed rotation and prevent the rotating shaft from bending.

A fourth aspect of the present invention aims to provide a fan motor capable of maintaining a constant air gap between a bearing and a rotating shaft to align the rotating shaft.

A fifth aspect of the present invention aims to provide a fan motor that can effectively prevent foreign matter such as dust from entering a gap formed between a bearing supporting the rotating shaft and the rotating shaft using air flowing around the rotating shaft.

A sixth aspect of the present invention aims to provide a fan motor that ensures stability and durability of a structure that utilizes air flowing around a rotating shaft to block the entry of foreign matter such as dust formed between the bearing and the rotating shaft. gap.

In order to achieve the aforementioned first and second objects, a fan motor according to the present invention may include: a shroud; a rotating shaft rotatably disposed on a straight line passing through the inner center of the shroud; an impeller, rotatably coupled to one end of the rotating shaft member; a rotor disposed on the rotating shaft; On the rotating shaft member, it is spaced axially from the impeller; an air bearing is lubricated with air and has an air gap with the rotating shaft member to rotatably support one side of the rotating shaft member; and a ball The bearing is coupled to the other end of the rotating shaft on the opposite side of the air bearing, and the rotor is interposed between the ball bearing and the air bearing to rotatably support the other side of the rotating shaft.

According to an example related to the present invention, the air bearing may be disposed between the impeller and the rotor toward the downstream side of the impeller with respect to the direction of air flow generated by the impeller.

According to an example related to the present invention, the rotating shaft member may include: a first supporting part supported by the air bearing; a second supporting part supported by the ball bearing; and a permanent magnet mounting part disposed on the first A permanent magnet is installed between a supporting part and the second supporting part.

In order to achieve the aforementioned third object, according to examples related to the present invention, the diameter of the first support part may be larger than the diameter of the second support part.

According to an example related to the present invention, the diameter of the first supporting part may be larger than the diameter of the permanent magnet mounting part.

According to an example related to the present invention, the fan motor may include a stator having a stator core and a stator coil. The stator core is disposed to surround the rotor and has an air gap therebetween. The stator coil is wound around the rotor. A stator core, wherein the inner diameter of the air bearing is configured to be smaller than the inner diameter of the stator core.

According to this configuration, the assembleability of the motor can be ensured.

According to an example related to the present invention, the inner diameter of the air bearing may be configured to be larger than the inner diameter of the rotor.

In order to achieve the aforementioned fourth object, according to an example related to the present invention, the fan motor may include: a first O-ring bracket installed on the outer circumferential surface of the air bearing to surround the air bearing; and a plurality of first O-ring brackets. An O-ring is respectively installed in a plurality of first O-ring mounting grooves provided on the first O-ring bracket.

According to an example related to the present invention, the fan motor may include: a second O-ring bracket installed on the outer circumferential surface of the ball bearing to surround the ball bearing; and a plurality of second O-rings installed respectively. In a plurality of second O-ring mounting grooves provided on the second O-ring bracket.

In order to achieve the foregoing fifth object, according to an example related to the present invention, the fan motor may include a first bearing housing disposed on a side of the impeller relative to the direction of the airflow generated by the impeller. The downstream side is provided with a first bearing receiving portion for accommodating the air bearing, wherein the impeller includes a hub and a plurality of blades protruding from the outer circumferential surface of the hub, and the hub is arranged to cover the opening of the impeller. The upper part of the air bearing.

According to an example related to the present invention, the fan motor may include: a first bearing housing disposed on a downstream side of the impeller with respect to the direction of air flow generated by the impeller, and provided with a first bearing housing accommodating the air bearing. Bearing receiving portion; a first vane hub, disposed on the downstream side of the first bearing housing relative to the air flow direction to cover a portion of the first bearing housing, and is provided with a plurality of third vane hubs for guiding the air flow. A fan blade; and a second fan blade hub, which is arranged on the downstream side of the first fan blade hub with respect to the air flow direction, and is provided with a plurality of second fan blades that guide the air flow.

According to examples related to the present invention, the first impeller hub and the second impeller hub may be defined as cylindrical shapes with the same diameter, and may be disposed on a straight line in the axial direction.

According to examples related to the present invention, the plurality of first fan blades and the plurality of second fan blades may be installed, coupled and supported on the inner circumferential surface of the guard.

According to an example related to the present invention, the fan motor may include a stator having a stator core and a stator coil. The stator core is disposed to surround the rotor and has an air gap with the rotor. The stator coil is wound The stator core, wherein the stator is coupled to make surface contact with the inner circumferential surface of the second blade hub to increase the heat between the stator and the air through the second blade hub and the plurality of second blades. exchange area.

According to an example related to the present invention, the second blade hub and the plurality of second blades may be formed of a thermally conductive metal material.

According to an example related to the present invention, the fan motor may further include: a first fastening portion protruding downward from the first bearing housing in an axial direction; and a second fastening portion axially protruding from the second bearing housing. The fan hub protrudes upward, wherein the first fastening part and the second fastening part are arranged to overlap with the first fan hub in the radial direction, and the first bearing housing, the first fan The impeller hub and the second impeller hub are fastened by a fastening member passing through the first fastening part, the first impeller hub and the second fastening part.

According to an example related to the present invention, the fan motor may further include a second bearing housing disposed on a downstream side of the rotor with respect to the air flow direction and provided with a second bearing receiving portion accommodating the ball bearing, wherein The second bearing housing includes a plurality of bridges receiving A portion protrudes toward the inner circumferential surface of the second impeller hub to connect the second bearing receiving portion and the second impeller hub.

In order to achieve the aforementioned first and second objects, a fan motor according to the present invention may include: a shroud; an impeller rotatably disposed inside the shroud to suck air into the shroud; and a rotating shaft a member, one end of which is coupled to the impeller and arranged to pass axially through the center of the shroud; a rotor arranged to be axially spaced apart from the impeller and provided with a rotary shaft member mounted on the rotating shaft member; a permanent magnet; a stator arranged inside the shield to surround the rotor and with a gap between it and the rotor; a first fan blade arranged between the impeller and the stator to guide the The air sucked by the impeller flows to the stator; an air bearing is arranged between the impeller and the rotor and is lubricated with air, and there is an air gap between one side of the rotating shaft and the air bearing so that it can rotate One side supporting the rotating shaft member; and a ball bearing disposed on the opposite side of the impeller relative to the rotor to rotatably support the other side of the rotating shaft member.

In order to achieve the aforementioned first and second objects, a rotor assembly according to the present invention includes: a rotating shaft member having a first supporting portion and a second supporting portion spaced apart from each other in the axial direction; and a permanent magnet mounting portion , is arranged between the first support part and the second support part; an impeller is arranged at one end of the rotating shaft; an air bearing is arranged adjacent to the impeller to be lubricated with air and connected with the third There is an air gap between a support part to rotatably support the first support part; a permanent magnet installed on the permanent magnet mounting part; and a ball bearing provided between the rotating shaft and the first support part The other end of the opposite side, and the permanent magnet is interposed between the ball bearing and the first supporting part to rotatably support the second supporting part.

According to examples related to the present invention, the air bearing may be implemented in polyaryl ether ketone (PAEK) or polyether ether ketone (PEEK) materials.

In order to achieve the foregoing fourth object, according to examples related to the present invention, the fan motor may include: a first O-ring mounting groove disposed on the outer circumferential surface of the air bearing along the circumferential direction; and a first O-ring mounting groove. ring, installed in the first O-ring installation groove.

According to an example related to the present invention, a plurality of the first O-ring mounting grooves may be provided spaced apart along the length direction of the air bearing, and a plurality of the first O-rings may be respectively installed on the first O-rings. Ring installation groove.

According to an example related to the present invention, the inner diameter of the air bearing may be configured to be larger than the length of the air bearing.

According to an example related to the present invention, the inner diameter of the air bearing may be configured to be smaller than the inner diameter of the stator core surrounding the permanent magnet.

In order to achieve the aforementioned third object, according to examples related to the present invention, the diameter of the first support part may be configured to be larger than the diameter of the second support part.

According to an example related to the present invention, the diameter of the first supporting part may be configured to be larger than the diameter of the permanent magnet mounting part.

According to an example related to the present invention, the fan motor may include: an O-ring bracket installed to surround the ball bearing and provided with a plurality of second O-ring mounting grooves on its outer wall; and a plurality of second O-ring brackets. rings, respectively installed in the plurality of second O-ring installation grooves.

In order to achieve the aforementioned fifth object, according to an example related to the present invention, the impeller may include: a hub; and a plurality of blades protruding from the outer circumferential surface of the hub, wherein the hub is arranged to overlap the air bearing in the axial direction , to cover the air bearing.

In order to achieve the aforementioned first and second objects, the fan motor according to the present invention may include: a shroud having a suction port and a first discharge port respectively at the upstream end and the downstream end in the air flow direction; The impeller is rotatably disposed inside the shroud; a rotating shaft has one end coupled to the impeller and is provided with a first support portion and a second support portion, the first support portion is disposed adjacent to The impeller, the second support part is axially spaced from the first support part; a permanent magnet is disposed between the first support part and the second support part and is rotatably mounted with the rotating shaft. Together; the stator has a stator core and a stator coil, the stator core surrounds the permanent magnet and has an air gap with the permanent magnet, and the stator coil wraps around the stator core; an air bearing, rotatably supporting the first supporting part; and a ball bearing rotatably supporting the second supporting part.

According to an example related to the present invention, the air bearing may be spaced with an air gap between the inner circumferential surface and the first support portion to be lubricated by air, and may be made of polyaryl ether ketone (PAEK) or polyether Etherketone (PEEK) material implementation.

According to an example related to the present invention, the fan motor may include: a first bearing receiving portion disposed between the impeller and the stator to accommodate the air bearing; and a motor housing disposed on the first bearing along the air flow direction. the downstream side of the bearing receiving portion to surround the stator core; an impeller hub, accommodated inside the shroud, one side of which surrounds the first bearing receiving portion and the other side of which surrounds the motor housing; a plurality of Fan blades protrude from the outer circumferential surface of the fan hub to be installed and coupled to the shroud. an inner circumferential surface; and a second bearing receiving portion accommodated inside the motor housing to accommodate the ball bearing.

According to an example related to the present invention, the fan motor may further include: an external channel defined as an annular shape and located between the shroud and the fan hub to transmit a portion of the air sucked by the impeller from the suction port to the first discharge outlet; an internal channel provided inside the fan hub and the motor housing; and a plurality of communication holes provided in the fan hub to communicate the external channel and the internal channel, so that Another part of the air flows into the inner channel from the upstream side of the outer channel.

According to an example related to the present invention, the fan motor may further include: a plurality of first bridges extending from an upper end of the motor housing to the first bearing receiving portion to connect the first bearing receiving portion and the motor housing. ; A plurality of second bridges extending radially from the outer circumferential surface of the second bearing receiving portion toward the inner circumferential surface of the motor housing to connect the motor housing and the second bearing receiving portion; and a plurality of A second discharge port is provided inside the motor housing to communicate with the internal passage to discharge air flowing along the internal passage and is provided between the plurality of second bridges.

According to an example related to the present invention, a plurality of fastening grooves may be respectively provided in the plurality of second bridges, and a plurality of fastening holes may be provided to radially engage with the plurality of fastening holes in the motor housing. The slots overlap, and the motor housing and the second bridges may be coupled to each other through a plurality of fastening members, and the plurality of fastening members are respectively fastened to the plurality of fastening slots through a plurality of fastening holes.

According to an example related to the present invention, the fan motor may further include: a plurality of fastening parts protruding radially from the outer circumferential surface of the motor housing toward the inner circumferential surface of the shroud to fasten the shroud and In the motor housing, a plurality of the first discharge ports are disposed between the plurality of fastening parts.

According to an example related to the present invention, the plurality of fastening portions and the plurality of second bridges may be disposed not to overlap each other in a radial direction on the outside and inside of the motor housing, and to be disposed with each other in a circumferential direction of the motor housing. alternately spaced.

In order to achieve the purpose of the present invention, a fan motor according to an embodiment of the present invention may include: a rotating shaft; an air bearing disposed to surround a portion of the rotating shaft, and a surface thereof facing the rotating shaft is in contact with the rotating shaft. The rotating shaft is spaced apart at a predetermined distance to form a gap for air to flow through; and a sealing portion is provided adjacent to the air bearing in the length direction of the rotating shaft to form a gap. Forming a part of the flow path of air in and out of the gap, and configured to block a part of the air flowing toward the gap along the circumference of the rotating shaft member.

The fan motor may further include: a housing part with an internal space for accommodating the air bearing, wherein the sealing part extends from the housing part toward the rotating shaft member, and one side of the sealing part is fixed to The other side of the housing part is spaced apart from the rotating shaft member by a predetermined distance to form a part of the flow path.

The sealing portion may be disposed on the upper side or lower side of the air bearing in the length direction of the rotating shaft member.

The sealing part may be provided in plural numbers and may include a first sealing member and a second sealing member, wherein the first sealing member is disposed closer to the air than the second sealing member in the length direction of the rotating shaft. bearings.

A first sealing gap is formed between the rotating shaft and the other side of the first sealing member facing the rotating shaft and the other side of the rotating shaft and the second sealing member facing the rotating shaft is formed. A second sealing gap between the sides can differ from each other.

The first sealing gap may be formed wider than the second sealing gap.

The sealing part may be provided in plural numbers and may include an upper sealing member and a lower sealing member, wherein the upper sealing member is disposed on the upper side of the air bearing in the length direction of the rotating shaft member, and the lower sealing member is on the upper side of the air bearing. The rotating shaft is arranged on the lower side of the air bearing in the length direction.

The housing part may have a groove part defined to be recessed on a surface facing the rotating shaft member to fix one side of the sealing part in the accommodated state.

The groove portion may be disposed to be inclined toward an outer area of the gap in a length direction of the rotating shaft member, and one side of the sealing portion may be received in the groove portion and may extend to be in the longitudinal direction of the rotating shaft member. The lengthwise direction slopes toward the outer region of the gap.

The sealing part may include: a first part constituting a part of the sealing part and made of a first material; and a second part constituting another part of the sealing part and made of a second material.

The first portion may be disposed to surround at least a portion of the second portion, and the second material may be stiffer than the first material.

The sealing part may include: a first part constituting one side of the sealing part, a part of the first part being received in the groove part and made of a first material; and a second part constituting the The other side of the sealing part is made of a second material different from the first material.

A first gap formed between the other side of the sealing portion and the rotating shaft member may be formed to be larger than a second gap formed between the rotating shaft member and a surface of the air bearing facing the rotating shaft member. narrow.

The fan motor may further include a housing part with an internal space for accommodating the air bearing, wherein the sealing part is provided with a slit, one side of the slit is fixed to the housing part, and the other side is fixed to The rotating shaft member, and the sealing portion are arranged to pass in a direction perpendicular to a surface facing the air bearing to form a part of the flow path, and the sealing portion outside the crack blocks air entering and exiting from the gap.

The sealing portion may be configured to have a C shape.

The crack may be configured to have a hole shape.

The sealing part may further include a mesh part disposed on the slit to divide the flow path into a plurality of areas.

The fan motor may further include a casing portion, which is provided with an internal space for accommodating the air bearing, wherein the sealing portions are provided in plural and include a casing seal member and a shaft seal member, and the casing seal The member is arranged to extend from the housing part toward the rotating shaft, one side of which is fixed to the housing part, and the other side is spaced apart from the rotating shaft by a predetermined distance, and one of the shaft sealing members One side is fixed to the rotating shaft, while the other side extends away from the rotating shaft to define a portion of the flow path with the housing sealing member.

The sealing portion may be arranged such that one side thereof is fixed to the rotating shaft member and the other side extends away from the rotating shaft member to form a part of the flow path.

The sealing portion may be made of the same type of material as the rotating shaft.

The sealing portion may comprise a curved portion disposed on the other side of the sealing portion forming part of the flow path to define a curved surface in the length direction of the rotating shaft member towards an outer region of the gap.

The sealing portion may include at least one of polytetrafluoroethylene (PTFE) and rubber.

The effects of the fan motor according to the present invention will be described below.

First, the air bearing may serve as a first bearing supporting a first support portion located adjacent to the rotating shaft member of the impeller.

Air bearings can be lubricated with air without the need for additional working fluid, so no friction occurs between the air bearing and the rotating shaft.

Therefore, even if the rotating shaft rotates at a high speed of more than 100,000 revolutions per minute, the friction between the air bearing and the rotating shaft may not cause wear, thereby extending the life of the bearing. In addition, air bearings can be applied to extend the life of the fan motor at high speeds.

Second, even if the air bearing diameter is increased, it can have the advantage of extending life.

Therefore, the diameter of the air bearing can be increased to increase the axial diameter of the first support portion.

In addition, the diameter (thickness) of the first support portion of the rotating shaft adjacent to the impeller may be increased (thickened) to prevent the rotating shaft from bending due to uneven load on the impeller during high-speed rotation. In addition, the thickness of the first support part can be increased to increase the limit speed allowed by the rotating shaft.

For example, the diameter of the first support portion may be set to be larger than the diameter of the impeller coupling portion of the rotation shaft member coupled with the impeller.

In addition, the diameter of the first support portion may be set to be larger than the diameter of the permanent magnet mounting portion of the rotating shaft member on which the permanent magnet is mounted.

Furthermore, the diameter of the first support part may be set larger than the diameter of the second support part supported by the second bearing.

Third, the rotating shaft member can be assembled such that the stator is pre-assembled to the inside of the shroud, and then the rotating shaft member is disposed between the first receiving portion and the second receiving portion of the shroud through the rotor receiving hole provided inside the stator core. on the same center line.

In order to couple the first supporting part to the inner circumferential surface of the first bearing through the rotor receiving hole, the diameter of the first supporting part may preferably be set smaller than the inner diameter of the stator core.

In addition, the inner diameter of the first bearing may be set smaller than the inner diameter of the stator core to ensure the assembleability of the rotating shaft member and the like. For example, when the ball bearing is coupled to the second support portion, the first support portion of the rotating shaft may be assembled to the inside of the air bearing.

Fourth, the air bearing may not be provided in the suction channel, expansion channel, and cooling channel that are the main channels of the fan motor, and the impeller may be provided to cover the first bearing receiving portion in which the air bearing is accommodated, thereby blocking foreign matter such as dust. Enter the air bearing.

Fifth, the first O-ring mounting groove can be provided on the outer wall of the first O-ring bracket surrounding the air bearing, and a plurality of first O-rings can be installed in a plurality of first O-ring mounting grooves, thereby Allow the rotating shaft to be axially aligned with the centerline of the shield.

Sixth, the first O-ring can be formed of an elastic material, thereby weakening the impact transmitted to the first bearing from the outside.

Seventh, the ball bearing may serve as a second bearing that supports the second support portion of the rotating shaft member located on the opposite side of the impeller relative to the permanent magnet mounting portion.

Since the second support portion of the rotating shaft located on the opposite side of the impeller is less affected by the uneven load of the impeller, the shaft diameter of the second support portion may be smaller than the shaft diameter of the first support portion.

Therefore, ball bearings can be applied to the second support part. Ball bearings are less expensive than air bearings. Therefore, in terms of cost, it is more advantageous to use one air bearing and one ball bearing than to use two air bearings to support both sides of the rotating shaft member.

Eighth, when only air bearings are used for two bearings, a thrust bearing should be used, which is a necessary component. However, when an air bearing and a ball bearing are applied, the use of a thrust bearing can be removed, thereby significantly reducing the size and weight of the fan motor.

Ninth, the first fan impeller hub and the second fan impeller hub may be arranged on a straight line with each other on the downstream side of the impeller relative to the direction of the airflow generated by the impeller, and be arranged between the shroud and the first fan impeller hub and the second fan impeller hub. The cooling channels between the impeller hubs can be set in a straight line without bending, thereby minimizing the flow resistance of the air and improving the cooling efficiency of the air to the motor.

Tenth, a plurality of second fan blades can be disposed on the outer circumferential surface of the second fan blade hub to protrude into the cooling channel, and the plurality of second fan blades not only guide the flow of air, but also increase the heat between the air and the stator. Swap area to maximize the motor's cooling performance.

Eleventh, the plurality of first fastening parts may protrude downward in the first bearing housing along the axial direction. The plurality of second fastening parts may protrude upward in the second impeller hub along the axial direction. The first fastening part and the second fastening part may be disposed to overlap with the first impeller hub in a radial direction. Fastening members such as screws can be fastened through the first fastening portion of the first bearing housing, the first impeller hub and the second fastening portion of the second bearing housing, so that the first bearing housing arranged in the axial direction The body, the first impeller hub and the second impeller hub are firmly fastened to each other, thereby significantly reducing the size and weight of the motor using a simple and compact fastening structure.

Twelfth, a plurality of fan blades protruding from the outer circumferential surface of the fan hub can be forcefully installed and coupled to the inner circumferential surface of the shroud, so that the shroud and the fan hub are firmly fastened to each other.

The first bearing receiving part and the motor housing may be integrated by a plurality of first bridges.

The fan hub and the motor housing may be arranged to overlap in a radial direction and be joined to each other through an adhesive, thereby firmly fastening each other.

Thirteenth, the plurality of fastening parts may protrude radially outward from the outer circumferential surface of the motor housing, and the plurality of fastening parts may be fastened to fastening members such as screws on the inner circumferential surface of the shield, thereby Allows the shroud and motor housing to be securely coupled to each other.

The second bearing receiving portion and the motor housing may be connected to each other through a plurality of second bridges, and the motor housing and the second bridge may be connected to each other through fastening members such as screws, thereby utilizing a simple and compact fastening structure. Reduce motor size and weight.

Fourteenth, the fastening positions between the guard and the fastening portion of the motor housing and the fastening positions between the motor housing and the second bridge of the second bearing receiving portion may be arranged to be spaced apart from each other in the circumferential direction open to have different phase angles, thereby ensuring the miniaturization and assembleability of the motor despite the small assembly space.

Fifteenth, the fan motor may include: an air bearing, a surface facing the rotating shaft member being spaced apart from the rotating shaft member by a predetermined distance to form a gap through which air flows; and a sealing portion configured to block the movement along the rotating shaft member. A part of the air flows toward the gap formed between the air bearing and the rotating shaft member, and at the same time forms a part of the flow path of the air in and out of the gap between the air bearing and the rotating shaft member.

Therefore, the air entering and exiting the gap can effectively flow through the area not blocked by the sealing portion, thereby allowing the air bearing to operate stably. In addition, a part of the air flowing into the gap can be blocked by the sealing portion, thereby greatly reducing the possibility of foreign matter such as dust flowing into the gap between the air bearing and the rotating shaft along with the air flow. Therefore, it is possible to prevent damage caused by dust flowing into the operating area of the bearing using the air flowing around the rotating shaft, and the reliability of the operation of the fan motor can be greatly improved.

Sixteenth, one side of the sealing part can be fixed while a part of the sealing part is accommodated in a groove part provided to be recessed on a surface of the housing part facing the rotating shaft member, thereby further ensuring that the sealing part Tectonic stability. Furthermore, the sealing part may consist of a first part and a second part made of different first and second materials, respectively, and the first part may be arranged to surround the second part. Here, the rigidity of the second material constituting the second portion surrounded by the first portion may be configured to be higher than the rigidity of the first material, thereby further improving the durability of the sealing portion.

100:shield

101:Suction port

102:First receiving department

103:Extended channel

104:Second receiving department

105: Cooling channel

106:Discharge outlet

107: Confirmation window

110:Rotating shaft parts

111: Impeller coupling part

112: First support part

113:Permanent magnet mounting department

114: Second support part

120: Impeller

121:wheel hub

122:Blade

130:Stator

131:Stator core

132:Back yoke

133: Teeth

134:Stator coil

135:Connecting ring

136:Bus

137:Insulator

140:Rotor

141:Permanent magnet

142: End cap

150:First bearing housing

151: First bearing receiving part

152: First axial movement restriction part

153:First buckle receiving slot

154: First fastening part

155:Second fastening hole

160:First fan impeller hub

161:First fan blade

162:First fastening hole

163:Second fan impeller hub

164:Second fan blade

165: Second fastening part

166:Third fastening hole

170: Second bearing housing

171: Second bearing receiving part

172:Bridge

173: Second axial movement restriction part

174:Second buckle receiving slot

180:Air bearing

181: First O-ring bracket

182: First O-ring installation groove

183:First O-ring

190:Ball bearing

191: Second O-ring bracket

192:Second O-ring installation groove

193:Second O-ring

200:shield

201:Suction port

202:First receiving department

203:Second receiving department

204:First row exit

205: First fastening hole

210: Impeller

211:wheel hub

212:Blade

213: concave part

220:Rotating shaft parts

221:Impeller coupling part

222:Shaft connection part

223: First support part

224:Permanent magnet mounting department

225: Second support part

226: First bearing receiving part

227: First axial movement restriction part

228:First buckle receiving slot

229:First buckle

230: Motor housing

231:First Bridge

232: Fastening part

233:First fastening groove

234: Second fastening hole

235:Internal channel

236:Connecting hole

237:Second row exit

238: around groove

240:Fan blade hub

241:Fan blade

242:Extended channel

243:External channel

250: Second bearing receiving part

251: Second axial movement restriction part

252:Second buckle receiving slot

253:Second buckle

254:Second Bridge

255:Second fastening groove

260,260': air bearing

261,261': First O-ring installation groove

262,262': First O-ring

270:Permanent magnet

271: End cap

280:Stator core

281:Back yoke

282:Tooth

283:Stator coil

284:Insulator

290:Ball bearing

291:O-ring bracket

292:Second O-ring installation groove

293:Second O-ring

300:Fan motor

310: Rotating shaft parts

310a:Central axis

311: Shaft groove

320:Bearing Department

320a: Gap

321: Bracket Department

321a: O-ring groove

321b:O-ring

322:Buckle

330:Sealing part

330a: Part One

330b:Part 2

331:Crack

332:Grid Department

333:Bending part

335a: Upper sealing member

335b: Lower sealing member

336a: first sealing member

336a1: First sealing gap

336b: Second sealing member

336b1: Second sealing gap

337a: Shell sealing component

337b: Shaft sealing component

340: Shell part

340a: Internal space

341: Groove part

341a: first groove

341b: Second groove

342:Buckle groove

351:Stator

351a:Stator core

351b: stator coil

351c:Insulator

352:Rotor

352a: Magnet Department

352b: End cap

361:Ball bearing

362: Ball bearing bracket

362a: Ball bearing O-ring

363: Ball bearing retaining ring

365: Ball bearing housing

371: Impeller

371a:wheel hub

371b: blade

371c:Through hole

372:Fan blade

372a: Fan blade body

380:Shield

380a: opening

d: inner diameter of air bearing

L: length of air bearing

a: air

a1: first airflow

a2: second airflow

g1: first gap

g2: second gap

D1: The length direction of the rotating shaft

D2: Radial direction of rotating shaft

FIG. 1 is a perspective view of the appearance of a fan motor according to an embodiment of the present invention.

FIG. 2 is an exploded view of the fan motor in FIG. 1 .

FIG. 3 is a cross-sectional view taken along line III-III in FIG. 1 .

FIG. 4 is a conceptual diagram showing a configuration in which the first bearing housing, the first impeller hub, and the second impeller hub in FIG. 3 are coupled to each other.

5 is a perspective view showing the configuration of the first O-ring bracket of FIG. 3 mounted to surround the outer surface of the air bearing.

FIG. 6 is an enlarged view of portion VI in FIG. 3 , which is a cross-sectional view showing a configuration in which the air bearing is mounted to the inside of the O-ring bracket.

FIG. 7 is a perspective view showing the appearance of a fan motor according to another embodiment of the present invention.

FIG. 8 is an exploded view of the fan motor in FIG. 7 .

FIG. 9 is a cross-sectional view taken along line IX-IX in FIG. 7 .

FIG. 10 is a perspective view showing the air bearing in FIG. 9 .

FIG. 11 is a cross-sectional view taken along line XI-XI in FIG. 10 , showing an arrangement in which the first O-ring is mounted on the outer circumferential surface of the air bearing.

12 is a perspective view showing a first O-ring mounting groove on an air bearing according to another embodiment of the present invention.

FIG. 13 is a cross-sectional view taken along line XIII-XIII in FIG. 12 , which shows the arrangement of a plurality of first O-rings mounted on the air bearing.

FIG. 14 is an exploded perspective view of a fan motor according to yet another embodiment of the present invention.

FIG. 15 is a perspective view showing the bearing part and the bracket part shown in FIG. 14 .

FIG. 16 is a perspective view showing the sealing portion in FIG. 14 .

17 to 22 are views showing other examples of the sealing portion shown in FIG. 16 .

FIG. 23 is a cross-sectional view showing the arrangement of the fan motor shown in FIG. 14 in an assembled state.

FIG. 24 is a partial enlarged view showing a portion of the motor assembly shown in FIG. 23 around the bearing portion.

FIG. 25 is a view showing the internal space of the housing part except the bearing part and the retaining ring shown in FIG. 24 .

FIG. 26 is a conceptual diagram showing an enlarged portion of the fan motor shown in FIG. 24 around the bearing portion.

27 to 34 are conceptual diagrams showing other examples of the fan motor shown in FIG. 26 .

The embodiments disclosed herein will be described in detail below with reference to the accompanying drawings. Regardless of the symbols in the drawings, the same or similar elements are represented by the same element symbols, and repeated descriptions thereof will be omitted. In the following description, the suffixes "module" and "unit" used to constitute components are only intended to facilitate the description of this specification, and the suffixes themselves do not have any special meaning or function. In addition, when describing the embodiments disclosed herein, if it is judged that the detailed description of the well-known technology to which the present invention belongs will obscure the gist of the present invention, the detailed description will be omitted. In addition, it should be understood that the accompanying drawings are only shown to facilitate the explanation of the concept of the present invention, and therefore it should not be understood that the disclosed technical concepts are limited by the attached drawings, and the interpretation of the concept of the present invention should be extended to include those disclosed herein. All modifications, equivalents and substitutes within the concept and technical scope of the invention.

It should be understood that, although the terms first, second, etc. may be used herein to describe various elements, these elements should not be limited by these terms. These terms are only used to distinguish one element from another element.

It will be understood that when an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may be present between the two elements. In contrast, when one element is "directly connected" or "directly coupled" to another element, it will be understood that there are no other elements between the two elements.

The singular includes the plural unless the context clearly indicates otherwise.

The terms "comprising" or "having" used herein shall be understood to mean that the presence of the features, quantities, steps, constituent elements, components or combinations thereof disclosed in this specification, and may also be understood to mean that the presence or addition of one or more is not excluded in advance. The possibility of multiple other features, numbers, steps, constituent elements, components or combinations thereof.

Figure 1 is a perspective view of the appearance of a fan motor according to the present invention.

FIG. 2 is an exploded view of the fan motor in FIG. 1 .

FIG. 3 is a cross-sectional view taken along line III-III in FIG. 1 .

FIG. 4 is a conceptual diagram showing a configuration in which the first bearing housing 150 , the first blade hub 160 and the second blade hub 163 in FIG. 3 are coupled to each other.

Figure 5 shows the first O-ring bracket 181 of Figure 3 installed to surround the air bearing 180 A perspective view of the configuration of the outer surface.

FIG. 6 is an enlarged view of portion VI in FIG. 3 , showing a cross-sectional view of the arrangement in which the air bearing 180 is mounted to the inside of the O-ring bracket.

The fan motor according to the present invention may include a shroud 100, a rotating shaft 110, an impeller 120, a first bearing housing 150, a first impeller hub 160, a second impeller hub 163, a second bearing housing 170, and a stator 130 , rotor 140, air bearing 180, and ball bearing 190.

The shroud 100 defines the appearance of the fan motor. The shield 100 has a circular cross-sectional shape.

The interior of the shield 100 has a receiving space.

The shield 100 can be divided into a suction port 101, a first receiving part 102, a second receiving part 104, and a discharge port 106 along the length direction (up and down direction or axial direction).

The suction port 101 and the first receiving portion 102 may be defined in a conical shape. The second receiving portion 104 may be defined as cylindrical.

The suction port 101 is provided at the upper end of the shield 100 . External air can be sucked into the shield 100 through the suction port 101 .

A bottle neck having a narrow cross-sectional area may be formed on the downstream side of the suction port 101 with respect to the air flow direction. The rate of air flow in the neck of the bottle can be increased to increase the pumping rate.

The first receiving portion 102 is provided on the downstream side of the suction port 101 with respect to the air flow direction.

The second receiving part 104 is provided on the downstream side of the first receiving part 102 with respect to the air flow direction.

The impeller 120 and the first bearing housing 150 may be received in the first receiving portion 102 .

The first receiving portion 102 may be defined such that the cross-sectional area gradually increases from the bottle neck to the second receiving portion 104 . The outer circumferential surface of the first receiving portion 102 may be disposed to be inclined from the bottle neck toward the second receiving portion 104 .

The second receiving part 104 may be provided on the downstream side of the first receiving part 102 .

The second receiving portion 104 may be defined as a cylindrical shape having a diameter larger than the diameter of the suction port 101 .

The first impeller hub 160 and the second impeller hub 163 may be received in the second receiving part 104 .

The stator 130 may be accommodated inside the second blade hub 163 .

The second bearing housing 170 may be accommodated inside the second impeller hub 163 .

The discharge port 106 is provided at the lower end of the second receiving part 104 . The discharge port 106 is configured to discharge the air inside the second receiving part 104 to the outside.

The rotating shaft 110 is disposed through the center of the shield 100 along the center line of the shield 100 in the axial direction.

The impeller 120 is configured to suck in outside air.

The impeller 120 includes a hub 121 and a plurality of blades 122 .

The hub 121 is located at the center of the impeller 120 . The hub 121 may be defined as a cone with a diameter that increases from an upper end to a lower end.

A plurality of blades 122 may be provided to protrude in a spiral shape on the outer circumferential surface of the hub 121 . A plurality of blades 122 may be provided to be spaced apart in the circumferential direction of the hub 121 .

The plurality of blades 122 may be defined such that the distance between them increases from the upper end to the lower end of the hub 121 .

The plurality of blades 122 may be spaced apart from the first receiving portion 102 by a certain distance.

A suction channel may be provided between the first receiving portion 102 and the hub 121 .

The impeller coupling part 111 may be provided at one end of the rotating shaft member 110 . The impeller 120 may be coupled to one end of the rotating shaft 110 to rotate together with the rotating shaft 110 .

When the impeller 120 rotates, external air may flow in along the suction channel of the shroud 100 through the suction port 101 .

The rotating shaft member 110 may include a first supporting part 112, a permanent magnet mounting part 113, and a second supporting part 114, these elements being defined with different diameters from an upper end to a lower end along the axial direction.

The first support portion 112 has the largest diameter. The first supporting portion 112 is located adjacent to the impeller coupling portion 111 .

The first bearing is coupled to the first support portion 112 . The first bearing may be embodied as an air bearing 180 .

The first bearing is configured to rotatably support the first supporting portion 112 of the rotating shaft 110 .

The permanent magnet mounting part 113 is located between the first supporting part 112 and the second supporting part 114 .

The diameter of the permanent magnet mounting part 113 may be smaller than the diameter of the first supporting part 112 .

The permanent magnets 141 of the rotor 140 are mounted on the permanent magnet mounting portion 113 so as to surround the outer circumferential surface of the permanent magnet mounting portion 113 .

The diameter of the second supporting part 114 is smaller than the diameter of the permanent magnet mounting part 113 .

The second bearing is coupled to the second support portion 114 . The second bearing can be embodied as a ball bearing 190 .

The second bearing is provided to rotatably support the second support portion 114 of the rotation shaft 110 .

The first supporting part 112 and the second supporting part 114 may be provided at the upper and lower parts of the rotating shaft member 110, with the permanent magnet mounting part 113 interposed therebetween. The second support portion 114 may be axially located on an opposite side of the impeller coupling portion 111 .

The first bearing housing 150 is provided on the downstream side of the impeller 120 and is spaced apart by a predetermined distance.

The first bearing housing 150 may be defined as a combination of conical and cylindrical shapes.

The upstream side of the first bearing housing 150 may be defined as a conical shape, and the downstream side of the first bearing housing 150 may be defined as a cylindrical shape.

The first bearing receiving portion 151 is provided to be recessed in the center portion of the first bearing housing 150 .

The first bearing receiving portion 151 may be provided to be open toward the impeller 120 .

The first bearing receiving portion 151 may be provided to pass therethrough in the axial direction.

The diameter of the first bearing receiving part 151 may be larger than the diameter of the first supporting part 112 and the diameter of the first bearing.

The first bearing receiving portion 151 may be defined as cylindrical. The first bearing may be received in the first bearing receiving portion 151 .

The first axial movement restricting portion 152 may extend from a lower end of the first bearing receiving portion 151 to a radially inner side thereof.

A through hole may be provided inside the first axial movement restricting part 152 . The diameter of the through hole may be set larger than the diameter of the first support part 112 and smaller than the diameter of the first bearing.

According to this configuration, when the first bearing is accommodated in the first bearing receiving portion 151 , the first axial movement restricting portion 152 can restrict the axial movement toward the rotor 140 .

The first buckle receiving groove 153 may be disposed radially outward from an upper end of the first bearing receiving portion 151 .

The first buckle receiving groove 153 is mounted to receive a buckle (not shown) therein. The buckle can be defined as a "C" shape. The buckle is defined as an annular shape that is open on one side and is elastically deformable so that the open area inside the buckle expands or contracts in the radial direction.

The buckle can prevent the first bearing from moving toward the blade when it is received in the first buckle receiving groove 153. The wheel 120 is axially separated from the first bearing receiver 151 .

The impeller 120 is disposed to overlap the first bearing housing 150 in the axial direction to cover the first bearing receiving portion 151 .

The first bearing housing 150 may be defined in a conical shape such that its diameter gradually increases from the upstream side to the downstream side with respect to the air flow direction.

The rate at which the diameter increases in the axial direction from the top toward the bottom of the first bearing housing 150 is greater than the rate at which the diameter increases from the upper end toward the lower end of the hub 121 .

The inclination of the outer surface of the hub 121 is greater than the inclination of the outer surface of the first bearing housing 150 .

The diameter of the upper end of the first bearing housing 150 is slightly larger than the diameter of the lower end of the hub 121 but is defined to increase at a rate similar to the increase in diameter of the first bearing housing 150 .

According to this configuration, the flow resistance of air can be minimized.

The expansion channel 103 may be provided between the first receiving portion 102 and the first bearing housing 150 . The expansion passage 103 is a passage for delivering air sucked from the suction passage to the first blade 161 which will be described later. The expansion channel 103 may be provided such that the diameter of the channel increases from the impeller 120 to the first blade 161 .

The first impeller hub 160 is configured to surround a portion of the outer surface of the first bearing housing 150 .

The upper part of the first impeller hub 160 may surround the first bearing housing 150 , and the lower part of the first impeller hub 160 may be defined as a cylinder having a constant diameter along the axial direction.

The connecting ring 135 may be installed on the inner circumferential surface of the lower part of the first blade hub 160 . The lower part of the first impeller hub 160 is arranged to surround the circular connecting ring 135 . The connecting ring 135 is configured to connect one end (neutral wire) of the three-phase stator coil 134 .

The surrounding groove may be recessed on the outer surface of the first bearing housing 150 with a depth equal to the thickness of the first impeller hub 160 . Therefore, the first impeller hub 160 is inserted into the surrounding groove, so that there is no step difference between the first bearing housing 150 and the first impeller hub 160 .

The first impeller hub 160 and the first bearing housing 150 may be joined by surrounding grooves.

A plurality of first blades 161 may be disposed on the outer circumferential surface of the first blade hub 160 to protrude in a spiral direction.

A plurality of first fan blades 161 are arranged at intervals along the circumferential direction of the first fan blade hub 160 open.

The first blade hub 160 and the first blade 161 may be integrally formed of insulating plastic material. The first fan blade 161 is configured to guide the air flowing in through the expansion channel 103 to the second fan blade 164 .

The plurality of first fan blades 161 may be coupled to the interior of the second receiving portion 104 of the guard 100 in a force-fitting manner.

The second blade hub 163 is provided on the downstream side of the first blade hub 160 .

The second impeller hub 163 may be defined as a cylindrical shape.

The second impeller hub 163 is configured to surround the stator 130 .

The stator 130 may be installed to be received inside the second impeller hub 163 .

The stator 130 can be bonded to the inner circumferential surface of the upper part of the second impeller hub 163 through adhesive components such as adhesive.

The stator 130 includes a stator core 131 and a stator coil 134 .

The stator core 131 may include a back yoke 132 and a plurality of teeth 133 .

Back yoke 132 may define an annular shape. Each of the plurality of teeth 133 is disposed to protrude from the inner surface of the back yoke 132 toward the center of the back yoke 132 .

A plurality of teeth 133 may be provided to be detachable from the rear yoke 132 . In this embodiment, the plurality of teeth 133 may have three teeth.

The coupling protrusion may be provided to protrude from one end of each of the plurality of teeth 133 .

The coupling protrusion may be slidably coupled in the axial direction along a coupling groove provided inside the rear yoke 132 .

The pole piece may be provided to protrude in the circumferential direction at the other end of each of the plurality of teeth 133 . A plurality of teeth 133 are provided to be spaced apart in the circumferential direction of the back yoke 132 .

Stator coil 134 may be configured as a three-phase coil. A plurality of stator coils 134 may be wound around the teeth 133 of each phase in the form of concentrated windings.

According to this configuration, not only the output of the motor can be improved, but also the size and weight of the motor can be reduced.

An insulator 137 insulating between the stator core 131 and the stator coil 134 may be inserted between the stator core 131 and the stator coil 134 . The insulators 137 may include a tooth insulator 137 disposed to surround a portion of the teeth 133 ; and a back yoke insulator 137 disposed to cover a portion of the back yoke 132 . Insulator 137 Made of insulating material such as plastic.

Rotor 140 includes permanent magnets 141 .

The permanent magnet 141 may be mounted on the outer circumferential surface of the permanent magnet mounting part 113 .

The permanent magnet mounting part 113 extends from the first support part 112 in the axial direction. The permanent magnet mounting part 113 may be provided to have a smaller diameter than the first supporting part 112 .

The permanent magnet 141 may be provided to have a smaller diameter than the inner diameter of the stator core 131 .

The inner diameter of the stator core 131 represents the diameter of the circumference passing through the inner ends of the plurality of pole pieces in the circumferential direction.

The permanent magnet 141 and the first support part 112 may be provided to have the same diameter.

The permanent magnet 141 may be rotatably mounted on the permanent magnet mounting portion 113 of the rotating shaft member 110 with a radially inward air gap relative to the pole piece of the stator core 131 .

In order to restrict the permanent magnet 141 from moving in the axial direction, the end cap 142 may be installed on the underside of the permanent magnet mounting part 113 . End cap 142 may define a cylindrical shape having the same diameter as permanent magnet 141 .

One side of the permanent magnet 141 may be in contact with the first supporting part 112 having a diameter larger than that of the permanent magnet mounting part 113, thereby restricting movement in the axial direction upstream.

The end cap 142 may restrict the other side of the permanent magnet 141 from moving axially downstream.

When three-phase alternating current is applied to each of the plurality of stator coils 134, the permanent magnets 141 may electromagnetic interact with the magnetic field generated around the stator coils 134 to generate a rotational force.

According to this configuration, the rotating shaft member 110 can rotate due to the electromagnetic interaction between the rotor 140 and the stator 130 .

A plurality of second blades 164 may be provided to protrude in a spiral direction on the outer circumferential surface of the second blade hub 163 .

A plurality of second blades 164 are arranged to be spaced apart along the circumferential direction of the second blade hub 163 .

The plurality of second fan blades 164 are configured to guide the air that has passed through the first fan blades 161 to the discharge port 106 .

The plurality of first fan blades 161 and the plurality of second fan blades 164 are arranged to be spaced apart in a straight line along the axial direction.

The cooling channel 105 may be provided between the second receiving part 104 and the first impeller hub 160 between.

The cooling channel 105 may be provided between the second receiving portion 104 and the second blade hub 163 .

The cooling channels 105 may be defined as axially straight to minimize flow resistance.

The cooling channel 105 is configured to cool the motor using air flowing from the expanded channel.

A plurality of second fan blades 164 are arranged to be received in the cooling channel 105 .

The plurality of second blades 164 may be integrally formed with the second blade hub 163 . The plurality of second blades 164 may be formed of the same metal material as the second blade hub 163 . The second blade hub 163 and the second blade 164 may be formed of aluminum or aluminum alloy materials with excellent thermal conductivity.

The plurality of second fan blades 164 can not only guide air, but also serve as heat sinks to dissipate the heat of the motor received through the second fan blade hub 163 to the cooling channel 105 .

The second impeller hub 163 can dissipate the heat transferred from the stator 130 to the cooling channel 105 through heat conduction.

For example, when current is applied to stator coil 134, stator coil 134 may generate heat. The heat generated from the stator coil 134 is heat conducted through the teeth 133 of the stator core 131 and the back yoke 132 , and is transferred to the second blade hub 163 .

A plurality of second fan blades 164 are configured to increase the heat exchange area with the air.

From the perspective of the flow path of the air, the air is sucked into the shield 100 through the suction port 101, and when flowing along the cooling channel 105 through the suction channel and the expansion channel 103, it is discharged to the outside through the discharge port 106.

The air flowing along the cooling channel 105 may exchange heat with the plurality of second blades 164 and the second blade hub 163 to cool the heat of the stator 130 .

The plurality of second fan blades 164 are coupled to the inner surface of the second receiving portion 104 of the guard 100 in a force-fitting manner.

The second bearing housing 170 is provided below the second blade hub 163 .

The second bearing housing 170 includes a second bearing receiving portion 171 in its inner center portion.

The second bearing receiving portion 171 may be defined as annular.

The second bearing is received in the second bearing receiving portion 171 .

The second bearing can be embodied as a ball bearing 190 .

The second axial movement limiting part 173 may be radially connected from an upper end of the second bearing receiving part 171 Extend inward.

A through hole may be provided inside the second axial movement restricting part 173 . The diameter of the through hole may be set larger than the diameters of the second support part 114 and the permanent magnet mounting part 113 .

The second axial movement limiting portion 173 may protrude radially inward and have an inner diameter smaller than the outer diameter of the second bearing. Therefore, the second bearing can limit axial movement toward the permanent magnet mounting portion 113 when accommodated in the second bearing receiving portion 171 .

The second bearing receiving portion 171 may be provided to be open downward.

The second buckle receiving groove 174 may be provided at the lower end of the second bearing receiving portion 171 to be recessed radially outward.

The buckle may be installed to be received in the second buckle receiving groove 174 .

The buckle ring can prevent the second bearing from being outwardly separated from the second bearing receiving portion 171 when received in the second buckle ring receiving groove 174 .

The second bearing housing 170 may include a plurality of bridges 172 .

A plurality of bridges 172 may be provided to protrude upward from the upper side of the second bearing receiving portion 171 toward the inner circumferential surface of the second blade hub 163 .

The upper end of each of the plurality of bridges 172 is in contact with the lower side of the inner circumferential surface of the second impeller hub 163 and can be joined to each other through an adhesive element such as an adhesive.

A plurality of bus bars 136 may be provided at the lower end of each of the plurality of bridges 172 .

A plurality of bus bars 136 are respectively connected to the three-phase stator coils 134 to apply three-phase alternating current.

The fastening structure of the first blade hub 160, the first bearing housing 150 and the second blade hub 163 will be described with reference to FIG. 4 .

The first impeller hub 160, the first bearing housing 150 and the second impeller hub 163 may be fastened to each other.

A plurality of first fastening holes 162 may be provided on the first impeller hub 160 .

A plurality of first fastening parts 154 may be provided to protrude downward at the lower end of the first bearing housing 150 . A plurality of first fastening parts 154 may be provided to be spaced apart in the circumferential direction of the first bearing housing 150 .

A plurality of second fastening holes 155 may be disposed to pass through a plurality of first fastening holes 155 in the thickness direction. Fastening part 154.

A plurality of second fastening parts 165 may be provided to protrude upward from the upper end of the second blade hub 163 . A plurality of second fastening parts 165 may be provided to be spaced apart along the circumferential direction of the second blade hub 163 .

A plurality of third fastening holes 166 may be provided to pass upward through the plurality of second fastening parts 165 along the thickness direction respectively.

The plurality of first fastening parts 154 and the plurality of second fastening parts 165 may be arranged to overlap along a thickness direction of the first fastening parts 154 (a direction perpendicular to the radial or axial direction of the first blade hub 160 ).

The second fastening part 165 may be provided to overlap on the inner circumferential surface of the first blade hub 160 in the thickness direction.

The first fastening portion 154 may be provided to overlap inside the second fastening portion 165 .

The plurality of first fastening holes 162 , the plurality of second fastening holes 155 and the plurality of third fastening holes 166 may be arranged to overlap along the thickness direction or radial direction of the first impeller hub 160 .

Fastening members such as screws may be coupled through the first fastening hole 162 , the second fastening hole 155 and the third fastening hole 166 so that the first blade hub 160 , the second blade hub 163 and the first bearing The housings 150 are fastened to each other.

The connecting ring mounting groove may be provided to be recessed on the upper side of the outer circumferential surface of the first fastening part 154 along the thickness direction. The connecting ring 135 can be inserted into the connecting ring mounting groove. The connecting ring 135 may be disposed between the first impeller hub 160 and the first fastening portion 154 of the first bearing housing 150 .

The fastening groove may be provided to be recessed on the lower side of the outer circumferential surface of the first fastening part 154 in the thickness direction. The second fastening part 165 may be inserted into the fastening groove.

The upper thickness of the first fastening portion 154 may be defined as equal to the sum of the lower thickness of the second fastening portion 165 and the lower thickness of the first fastening portion 154 .

The second fastening part 165 may be provided smaller than the thickness of the second impeller hub 163 .

The first impeller hub 160 may be disposed to surround the second fastening part 165 .

When installed to surround the second fastening portion 165 of the first impeller hub 160, the first impeller hub 160 and the second impeller hub 163 may be disposed to overlap in the axial direction without a step difference.

According to this configuration, the first fastening portion 154 of the first bearing housing 150, the first impeller hub 160, and the second fastening portion 165 of the second impeller hub 163 may be arranged to radially overlap from the inside to the outside thereof. , and the fastening member can be provided on the first fastening part 154, the first impeller hub 160 and the second The fastening holes in the fastening part 165 are fastened, and the first bearing housing 150, the first impeller hub 160 and the second impeller hub 163 can be made of a simple fastening structure, but can be firmly fastened to each other. and compactly designed to help reduce size and weight.

A plurality of confirmation windows 107 may be provided on one side of the side of the shield 100 along the thickness direction.

The confirmation window 107 may be disposed along the radial direction of the first fastening hole 162 , the second fastening hole 155 , the third fastening hole 166 and the shield 100 .

The first to third fastening holes 162 to 166 may be exposed through the confirmation window 107 .

The fastening members fastened to the first to third fastening holes 162 to 166 may be exposed through the confirmation window 107 .

When the rotating shaft 110 is not aligned with the center of the shield 100 along the axial direction, the rotating shaft 110 can be aligned through the confirmation window 107 .

For example, when one side of the rotating shaft 110 is twisted, a tool such as a driver can pass through the confirmation window 107 to press or rotate one side of the first blade hub 160 to align it in the axial direction.

Referring to FIGS. 5 and 6 , the first bearing supporting the first support part 112 may be implemented as an air bearing 180 .

Air bearing 180 may be defined as a hollow cylinder. The shaft receiving portion is provided inside the air bearing 180 .

The air bearing 180 is provided to form an air gap between the outer circumferential surface of the first support portion 112 and the inner circumferential surface of the air bearing 180 .

The air gap can be 0.04 mm or less.

In order to ensure the assembleability of the rotating shaft 110 and the rotor 140 , the inner diameter of the air bearing 180 may be set smaller than the inner diameter of the stator core 131 .

The inner diameter (d) of the air bearing 180 may be set larger than the length (height) of the air bearing 180 to reduce wear of the inner diameter surface of the air bearing 180 .

The inner diameter of the stator core 131 represents the diameter of a circle passing through the inner ends of the plurality of teeth 133 in the circumferential direction.

The ratio of the length (L) of the air bearing 180 to the inner diameter (d) of the air bearing 180 may be 0.7 or less. When the length/inner diameter ratio of the air bearing 180 exceeds 0.7, the amount of wear on the inner diameter surface of the air bearing 180 may increase significantly.

Since the air bearing 180 rotatably supports the rotating shaft member 110 in a non-lubricated state, a material having a low friction coefficient and excellent wear resistance is used.

For example, air bearing 180 may be made from polyetheretherketone (PEEK) or polyaryletherketone (PAEK) materials that have excellent non-lubricating friction characteristics and wear resistance.

PEEK or PAEK will cause little wear on the bearings after operation, and the gap between the PEEK and the shaft will change very little.

The air bearing 180 may form an air layer between the rotating shaft 110 and the inner circumferential surface of the air bearing 180, and support the rotating shaft 110 in a non-contact manner without additional working fluid such as lubricating oil.

The first O-ring bracket 181 may be installed on the outer circumferential surface of the first bearing to surround the outer circumferential surface of the first bearing.

The first O-ring bracket 181 may define a cylindrical shape.

The diameter of the first O-ring bracket 181 may be the same as or similar to the outer diameter of the first bearing.

The first bearing may be press fit to the inner circumferential surface of the first O-ring bracket 181 .

The first O-ring bracket 181 may be received in the first bearing receiver 151 .

The first O-ring mounting groove 182 may be provided to be radially recessed along the circumferential direction on the outer circumferential surface of the first O-ring support frame 181 .

The O-ring may be installed to be received in the first O-ring mounting groove 182 .

The plurality of first O-rings 183 may be made of elastic material such as rubber.

A plurality of first O-ring mounting grooves 182 may be provided on the outer circumferential surface of the first O-ring bracket 181 . In this embodiment, a configuration in which two first O-ring mounting grooves 182 are provided is shown.

A plurality of first O-ring mounting grooves 182 may be provided to be spaced apart along the axial direction of the first O-ring bracket 181 .

The plurality of first O-rings 183 may be in close contact with the first bearing receiving portion 151 .

According to this configuration, the plurality of first O-rings 183 can be aligned with the concentricity of the first bearing. The plurality of first O-rings 183 can prevent the first O-ring bracket 181 from rotating in the first bearing receiving portion 151 .

The plurality of first O-rings 183 can reduce vibration and impact transmitted to the first bearing from the outside.

The second bearing supporting the second support part 114 may be implemented as a ball bearing 190 .

The second O-ring bracket 191 may be installed on the outer circumferential surface of the ball bearing 190 to surround the ball bearing 190 .

A plurality of second O-ring mounting grooves 192 may be provided on the outer circumferential surface of the second O-ring bracket 191 . In this embodiment, a configuration in which two second O-ring mounting grooves 192 are provided is shown.

A plurality of second O-rings 193 may be installed in a plurality of second O-ring installation grooves 192 respectively.

A plurality of second O-rings 193 may be aligned with the concentricity of the second bearing. The plurality of second O-rings 193 can prevent the second O-ring bracket 191 from rotating relative to the second bearing receiving portion 171 .

The plurality of second O-rings 193 are made of elastic material such as rubber.

The plurality of second O-rings 193 can reduce vibration and impact transmitted to the first bearing from the outside.

The ball bearing 190 may be composed of an outer ring, an inner ring and a plurality of balls.

The outer ring is fixedly provided on the inner circumferential surface of the second O-ring bracket 191 . The inner ring is coupled to the outer circumferential surface of the second support portion 114 . A plurality of balls are interposed between the outer ring and the inner ring to support the relative rotational motion of the inner ring relative to the outer ring.

Therefore, according to the present invention, the air bearing 180 serves as a first bearing that supports the first support portion 112 of the rotation shaft 110 adjacent to the impeller 120 .

Since the air bearing 180 is lubricated by air and does not require additional working fluid, no friction occurs between the air bearing 180 and the rotating shaft 110 .

Therefore, even if the rotating shaft 110 rotates at a high speed of more than 100,000 revolutions per minute, the friction between the air bearing 180 and the rotating shaft 110 may not cause wear, thereby extending the life of the bearing. In addition, air bearings 180 can be applied to extend the life of the fan motor rotating at high speed.

Additionally, the air bearing 180 may have the advantage of extending its life even as its diameter increases.

Therefore, the diameter of the air bearing 180 may be increased to increase the axial diameter of the first support portion 112 .

In addition, the diameter (thickness) of the first support portion 112 of the rotating shaft member 110 adjacent to the impeller 120 may be increased (thickened) to prevent the rotating shaft member 110 from bending due to uneven load on the impeller 120 during high-speed rotation. In addition, the thickness of the first support portion 112 can be increased to increase the limit speed allowed by the rotating shaft 110 .

For example, the diameter of the first support portion 112 may be set to be larger than the diameter of the first support portion 112 coupled with the impeller 120 . The diameter of the impeller coupling portion 111 of the rotating shaft 110 .

In addition, the diameter of the first support portion 112 may be set to be larger than the diameter of the permanent magnet mounting portion 113 of the rotating shaft member 110 on which the permanent magnet 141 is mounted.

In addition, the diameter of the first support part 112 may be set larger than the diameter of the second support part 114 supported by the second bearing.

The rotating shaft member 110 can be assembled such that the stator 130 is pre-assembled to the inside of the shroud 100, and then the rotating shaft member 110 is disposed at the first receiving portion 102 and the second receiving portion 102 of the shroud 100 through the rotor receiving hole provided inside the stator core 131. The two receiving parts 104 are on the same center line.

In order to couple the first supporting part 112 to the inner circumferential surface of the first bearing through the rotor receiving hole, the diameter of the first supporting part 112 may preferably be set smaller than the inner diameter of the stator core 131 .

In addition, the inner diameter of the first bearing may be set smaller than the inner diameter of the stator core 131 to ensure the assemblability of the rotating shaft member 110 and the like.

In addition, the air bearing 180 may not be provided in the suction passage, the expansion passage 103 and the cooling passage 105 which are the main passages of the fan motor, and the impeller 120 may be provided to cover the first bearing receiving portion 151 that accommodates the air bearing 180, thereby blocking Foreign matter such as dust enters the air bearing 180 .

In addition, the first O-ring installation groove 182 may be provided on the outer wall of the first O-ring bracket 181 surrounding the air bearing 180, and a plurality of first O-rings 183 may be installed in a plurality of first O-ring installation grooves. 182, thereby allowing the rotating shaft 110 to be axially aligned with the centerline of the shield 100.

In addition, the first O-ring 183 may be formed of an elastic material, thereby weakening the impact transmitted to the first bearing from the outside.

At the same time, the ball bearing 190 may serve as a second bearing that supports the second supporting portion 114 of the rotating shaft member 110 located on the opposite side of the impeller 120 relative to the permanent magnet mounting portion 113 .

Since the second supporting portion 114 of the rotating shaft member 110 located on the opposite side of the impeller 120 is less affected by the uneven load of the impeller 120 , the shaft diameter of the second supporting portion 114 may be smaller than the shaft diameter of the first supporting portion 112 .

Therefore, the ball bearing 190 may be applied to the second support part 114 . Ball bearing 190 is cheaper than air bearing 180. Therefore, in terms of cost, it is more advantageous to use one air bearing 180 and one ball bearing 190 than to use two air bearings 180 to support both sides of the rotating shaft 110 .

In addition, when only the air bearing 180 is used for two bearings, a thrust bearing should be used, which is a necessary element. However, when an air bearing 180 and a ball bearing 190 are used, The thrust bearing can be removed, significantly reducing the size and weight of the fan motor.

In addition, the first impeller hub 160 and the second impeller hub 163 may be disposed on a straight line with each other on the downstream side of the impeller 120 with respect to the airflow direction generated by the impeller 120, and be disposed between the shroud 100 and the first impeller hub. The cooling channels 105 between the second fan hubs 163 can be arranged in a straight line without bending, thereby minimizing the flow resistance of the air and improving the cooling efficiency of the air to the motor.

In addition, a plurality of second fan blades 164 can be disposed on the outer circumferential surface of the second fan hub 163 to protrude into the cooling channel 105, and the plurality of second fan blades 164 can not only guide the flow of air, but also increase the interaction between the air and the stator. 130 heat exchange areas, thereby maximizing the motor’s cooling performance.

In addition, the plurality of first fastening parts 145 may protrude downward in the first bearing housing 150 along the axial direction. A plurality of second fastening parts 165 may protrude upward in the second impeller hub 163 along the axial direction. The first fastening part 154 and the second fastening part 165 may be disposed to overlap with the first impeller hub 160 in the radial direction. Fastening members such as screws can be fastened through the first fastening portion 154 of the first bearing housing 150, the first impeller hub 160, and the second fastening portion 165 of the second bearing housing 170, so that along the axial direction The first bearing housing 150, the first impeller hub 160 and the second impeller hub 163 are provided to be firmly fastened to each other, thereby greatly reducing the size and weight of the motor using a simple and compact fastening structure.

7 is a perspective view showing the appearance of the fan motor according to the present invention.

FIG. 8 is an exploded view of the fan motor in FIG. 7 .

FIG. 9 is a cross-sectional view taken along line III-III in FIG. 7 .

FIG. 10 is a perspective view showing the air bearing 260 in FIG. 9 .

FIG. 11 is a cross-sectional view taken along line XI-XI in FIG. 10 , showing the arrangement in which the first O-ring 262 is mounted on the outer circumferential surface of the air bearing 260 .

The fan motor according to the present invention may include a shroud 200, a rotating shaft 220, an impeller 210, a blade hub 240, a motor housing 230, a stator, a rotor, an air bearing 260, and a ball bearing 290.

The shroud 200 defines the appearance of the fan motor. The shield 200 has a circular cross-sectional shape.

The interior of the shield 200 has a receiving space.

The shield 200 can be divided into a suction port 201, a first receiving part 202, a second receiving part 203, and a first discharge port 204 along the length direction (up and down direction or axial direction).

The suction port 201 and the first receiving portion 202 may each be defined in a conical shape.

The second receiving portion 203 may be defined in a cylindrical shape. The first discharge outlet 204 can be set at The lower end of the shield 200.

The suction port 201 is provided at the upper end of the shield 200 . External air can be sucked into the shield 200 through the suction port 201.

The suction port 201 may be defined as an inverted cone.

A bottle neck having a narrow cross-sectional area may be formed on the downstream side of the suction port 201 with respect to the air flow direction. The rate of air flow in the neck of the bottle can be increased to increase the pumping rate.

The first receiving portion 202 is provided on the downstream side of the suction port 201 with respect to the air flow direction.

The second receiving part 203 is provided on the downstream side of the first receiving part 202 with respect to the air flow direction.

The impeller 210 and the first bearing receiver 226 may be received in the first receiver 202 .

The first receiving portion 202 may be defined such that the cross-sectional area gradually increases from the bottle neck to the second receiving portion 203 . The outer circumferential surface of the first receiving part 202 may be provided in a curved shape to be inclined from the bottle neck toward the second receiving part 203.

The second receiving part 203 may be defined as a cylindrical shape, the diameter of which is larger than the diameter of the suction port 201 or the upper end of the first receiving part 202 .

The fan hub 240 and the motor housing 230 may be received in the second receiving part 203 .

A plurality of fastening parts 232 may be provided at the lower end of the motor housing 230 .

The plurality of fastening parts 232 may be provided to protrude radially outward from the outer circumferential surface of the motor housing 230 toward the inner circumferential surface of the shroud 200 .

The outer circumference of the plurality of fastening parts 232 may extend to contact the inner circumferential surface of the shield 200 . The first fastening groove 233 may be disposed on each of the plurality of fastening parts 232 in a radial direction. A plurality of first fastening holes 205 may be provided at the lower end of the shield 200 to pass therethrough along the thickness direction. The first fastening hole 205 may be disposed to radially overlap the first fastening groove 233 .

A fastening member such as a screw may be fastened to the first fastening groove 233 of the fastening portion 232 through the first fastening hole 205 of the shield 200, thereby allowing the shield 200 and the motor housing 230 to be fastened to each other.

The stator may be housed inside the motor housing 230 .

The second bearing receiving portion 250 may be received inside the motor housing 230 .

The first discharge port 204 is provided at the lower end of the second receiving part 203 . The plurality of first discharge ports 204 may be provided between the plurality of fastening parts 232 protruding radially outward from the outer circumferential surface of the motor housing 230 .

The first discharge port 204 can discharge the air inside the second receiving part 203 to the outside.

The rotating shaft 220 is disposed through the center of the shield 200 along the center line of the shield 200 in the axial direction.

The impeller 210 is configured to suck in outside air.

The impeller 210 includes a hub 211 and a plurality of blades 212 .

The hub 211 is located at the center of the impeller 210 . The hub 211 may be defined as a cone with a diameter that increases from an upper end to a lower end.

The recess 213 may be provided at the lower part of the hub 211 . The recess 213 may be provided in a tapered shape that is concave toward the interior of the hub 211 . A portion of the rotation shaft 220 may be provided to be received in the recess 213 .

A fastening hole may be provided inside the hub 211 to fasten to one end of the rotating shaft 220 .

A plurality of blades 212 may be provided to protrude in a spiral shape on the outer circumferential surface of the hub 211 . A plurality of blades 212 may be provided to be spaced apart in the circumferential direction of the hub 211 .

The plurality of blades 212 may be defined with increasing distances from each other from the upper end to the lower end of the hub 211 .

The plurality of blades 212 may be spaced apart from the first receiving portion 202 by a certain distance.

The suction channel may be provided between the first receiving part 202 and the hub 211.

The rotating shaft 220 may include an impeller coupling part 221, a shaft connecting part 222, a first supporting part 223, a permanent magnet mounting part 224, and a second supporting part 225. These elements have different diameters from the upper end to the lower end in the axial direction. define.

The impeller coupling part 221 may be provided at one end of the rotating shaft member 220 . The impeller coupling part 221 may be coupled to the impeller 210 through the fastening hole, and the impeller 210 may rotate together with the rotation shaft member 220 .

The shaft connecting portion 222 may be provided to have a larger diameter than the impeller coupling portion 221 . When the impeller coupling part 221 is fastened to the fastening hole, the shaft connecting part 222 may be received in the recess 213 . One end of the shaft connecting portion 222 is in close contact with the recessed portion 213 to limit axial movement.

When the impeller 210 rotates, external air may flow in from the suction port 201 along the suction channel of the shroud 200 .

Among the portions of the rotating shaft member 220 having different diameters, the first support portion 223 has the largest diameter. The first supporting portion 223 is located adjacent to the impeller 210 .

The first bearing is coupled to the first support part 223 . The first bearing can be embodied as an air bearing 260.

The first bearing is configured to rotatably support the first supporting portion 223 of the rotating shaft 220 .

The permanent magnet mounting part 224 is located between the first supporting part 223 and the second supporting part 225 .

The diameter of the permanent magnet mounting part 224 may be smaller than the diameter of the first supporting part 223 .

The permanent magnets 270 of the rotor are mounted on the permanent magnet mounting portion 224 so as to surround the outer circumferential surface of the permanent magnet mounting portion 224 .

The diameter of the permanent magnet mounting part 224 is smaller than the diameter of the first supporting part 223 .

The diameter of the second supporting part 225 is smaller than the diameter of the permanent magnet mounting part 224 .

The second bearing is coupled to the second support portion 225 . The second bearing may be embodied as a ball bearing 290 .

The second bearing is configured to rotatably support the second supporting portion 225 of the rotating shaft 220 .

The ball bearing 290 may be composed of an outer ring, an inner ring and a plurality of balls.

The outer ring is fixedly provided on the inner circumferential surface of the O-ring bracket 291 . The inner ring is coupled to the outer circumferential surface of the second support portion 225 . A plurality of balls are inserted between the outer ring and the inner ring to support the relative rotation of the inner ring relative to the outer ring.

The first supporting part 223 and the second supporting part 225 may be provided at the upper and lower parts of the rotating shaft member 220, with the permanent magnet mounting part 224 interposed therebetween. The second support portion 225 may be axially located on an opposite side of the impeller coupling portion 221 .

The first bearing receiving portion 226 is provided on the downstream side of the impeller 210 and is spaced apart by a predetermined distance.

The first bearing receiver 226 may be defined as cylindrical. Air bearing 260 is received in first bearing receiver 226 .

The first bearing receiving portion 226 may be provided to open upward toward the impeller 210 .

The diameter of the first bearing receiving portion 226 may be larger than the diameter of the first support portion 223 and the diameter of the air bearing 260 .

The first axial movement limiting portion 227 may extend from a lower end of the first bearing receiving portion 226 to a radially inner side thereof.

A through hole may be provided inside the first axial movement restricting part 227 . The diameter of the through hole may be set larger than the diameter of the first support part 223 and smaller than the diameter of the air bearing 260 .

According to this configuration, when the air bearing 260 is accommodated in the first bearing receiving portion 226 When , the first axial movement limiting part 227 can limit the axial movement to the rotor.

The first buckle receiving groove 228 may be disposed radially outward from the upper end of the first bearing receiving portion 226 .

The first buckle receiving groove 228 is mounted to receive the first buckle 229 therein. The first buckle 229 may be defined as a "C" shape. The first buckle 229 is defined as an annular shape with one side open and can be elastically deformed to expand or contract the open area inside the first buckle 229 in the radial direction.

The first retaining ring 229 may be defined to be slightly larger than the first bearing receiving portion 226 to accommodate the outer diameter for insertion into the first retaining ring receiving groove 228 , and the inner diameter may be defined to be smaller than the air bearing 260 .

The first buckle ring 229 can prevent the air bearing 260 from being axially separated from the first bearing receiving portion 226 toward the impeller 210 when received in the first buckle ring receiving groove 228 .

The upper end portion of the first bearing receiving portion 226 is received in the recess 213 provided on the lower side of the hub 211 .

The hub 211 of the impeller 210 is disposed to overlap the first bearing receiving portion 226 in the axial direction, thereby covering the upper opening portion of the open first bearing receiving portion 226 .

According to this configuration, the hub 211 can block foreign matter such as dust in the air sucked through the impeller 210 from flowing into the air bearing 260 .

The blade hub 240 may be defined as a combination of a hollow conical shape and a cylindrical shape.

The cone part may be provided on the upper part of the fan hub 240 , and the cylindrical part may be provided on the lower part of the fan hub 240 .

The conical portion of the blade hub 240 may be defined as having a diameter that gradually increases from the upstream side to the downstream side with respect to the airflow direction.

The ratio of the diameter increasing in the axial direction from the top to the bottom of the conical portion of the fan hub 240 is greater than the ratio of the diameter increasing from the upper end to the lower end of the hub 211 .

In other words, the inclination of the outer surface of the hub 211 is greater than the inclination of the outer surface of the blade hub 240 .

The diameter of the upper end of the fan blade hub 240 may be defined to be slightly larger than the lower end of the hub 211 .

According to this configuration, the flow resistance of air can be minimized.

The expansion channel 242 may be disposed between the first receiving portion 202 and the blade hub 240 . The expansion passage 242 is a passage for conveying air sucked from the suction passage to a fan blade 241 which will be described later.

The expansion channel 242 may be provided such that the diameter of the channel increases from the impeller 210 toward the fan blade 241 .

The opening is provided at the upper end of the conical portion of the blade hub 240 . The upper end of the first bearing receiving portion 226 may protrude through the opening, and may be received in the conical portion of the blade hub 240 below the upper end of the first bearing receiving portion 226 .

The motor housing 230 is disposed on the downstream side of the blade hub 240 with respect to the air flow direction.

The outer circumferential surface of the motor housing 230 may be coupled to the inner circumferential surface of the blade hub 240 . The outer circumferential surface of the motor housing 230 and the inner circumferential surface of the fan hub 240 may be joined to each other through an adhesive element such as an adhesive.

The first bearing receiving portion 226 may be provided spaced apart on the upstream side of the motor housing 230 .

The first bearing receiving portion 226 and the motor housing 230 may be connected by a plurality of first bridges 231 .

One side of each of the plurality of first bridges 231 may be defined as connected to the outer circumferential surface of the first bearing receiving portion 226 , and the other side of each of the plurality of first bridges 231 may be defined as connected to the motor. The upper end of the housing 230.

Motor housing 230 is defined to have a diameter that is greater than the diameter of first bearing receiver 226 .

Each of the plurality of first bridges 231 may include a straight portion extending directly upward from the motor housing 230 and an inclined portion extending upward obliquely toward the outer circumferential surface of the first bearing receiving portion 226 .

A plurality of first bridges 231 may be provided spaced apart in a circumferential direction of the motor housing 230 or the first bearing receiving portion 226 .

The opening is located between the plurality of first bridges 231 and may be configured to open in a radial direction.

The conical portion and the cylindrical portion of the blade hub 240 are configured to cover the opening between the first bridges 231 . Parts of the conical portion and the cylindrical portion of the fan hub 240 may be disposed to surround a plurality of first bridges 231 and overlap in the radial and up-down directions.

An internal passage 235 may be axially disposed inside the blade hub 240 and inside the motor housing 230 to allow air to flow into the motor housing 230 .

A plurality of communication holes 236 may be provided in the conical portion of the blade hub 240 . plural The communication hole 236 may connect the expansion channel 242 of the first receiving part 202 and the internal channel 235 of the motor housing 230 to communicate with each other. A plurality of communication holes 236 may be provided spaced apart along the circumferential direction of the blade hub 240 .

According to this configuration, the air sucked by the impeller 210 can branch from the expansion passage 242 through the communication hole 236 to flow into the internal passage 235 of the motor housing 230 .

The cylindrical portion of the fan hub 240 may be defined as a cylindrical shape having a constant diameter along the axial direction.

The external channel 243 may be provided between the second receiving portion 203 and the outer circumferential surface of the cylindrical portion of the blade hub 240 .

The opening portion provided between the plurality of first bridges 231 may be provided to communicate with the communication hole 236 and may also be connected to communicate with the internal passage 235 .

The external channel 243 is provided on the downstream side of the expansion channel 242 . A part of the air sucked by the impeller 210 may flow from the expansion channel 242 into the inner channel 235 through the communication hole 236 , and the other part of the air sucked may flow from the expansion channel 242 to the outer channel 243 .

A connecting ring (not shown) may be installed on the inner circumferential surface of the fan hub 240 . The blade hub 240 is configured to surround the circular connecting ring. The connection ring is configured to connect one end (neutral wire) of the three-phase stator coil 283 .

The surrounding groove 238 may be provided on the outer circumferential surface of the motor housing 230 and be recessed with a depth equal to the thickness of the blade hub 240 . Therefore, the fan hub 240 is inserted into and coupled to the surrounding groove 238 so that there is no step difference between the motor housing 230 and the fan hub 240 .

Blade hub 240 and motor housing 230 may be joined by surrounding groove 238 .

A plurality of fan blades 241 may be disposed to protrude in a spiral direction on the outer circumferential surface of the fan blade hub 240 .

A plurality of fan blades 241 are arranged to be spaced apart along the circumferential direction of the fan blade hub 240 .

The fan hub 240 and the fan blade 241 can be integrally formed. The fan blades 241 are configured to guide air flowing in through the expansion channel 242 to the outer channel 243 .

The plurality of fan blades 241 may be coupled to the interior of the second receiving portion 203 of the guard 200 in a force-fitting manner.

Motor housing 230 is configured to surround the stator.

The stator may be installed for a press fit into the motor housing 230 .

The stator includes a stator core 280 and a stator coil 283 .

The stator core 280 may be bonded to the inner circumferential surface of the upper portion of the motor housing 230 through an adhesive element such as an adhesive.

The stator core 280 may include a back yoke 281 and a plurality of teeth 282 .

The back yoke 281 may be defined as annular. Each of the plurality of teeth 282 is disposed to protrude radially from the inner surface of the back yoke 281 toward the center of the back yoke 281 .

The plurality of teeth 282 may be configured to be detachable from the rear yoke 281 . In this embodiment, the plurality of teeth 282 may have three teeth.

The coupling protrusion may be provided to protrude from one end of each of the plurality of teeth 282 .

The coupling protrusion may be slidably coupled along the shaft along a coupling groove provided inside the rear yoke 281 .

The pole piece may be disposed to protrude in a circumferential direction of the other end of each of the plurality of teeth 282 . A plurality of teeth 282 are provided spaced apart in the circumferential direction of the back yoke 281 .

The stator coil 283 may be configured as a three-phase coil. A plurality of stator coils 283 may be wound around the teeth 282 of each phase in the form of concentrated windings.

According to this configuration, the tooth-divided core of the teeth 282 and the concentrated winding structure of the coil can not only increase the output of the motor, but also contribute to reducing the size and weight of the motor.

An insulator 284 insulating between the stator core 280 and the stator coil 283 may be inserted between the stator core 280 and the stator coil 283 . The insulators 284 may include a tooth insulator 284 disposed to surround a portion of the teeth 282 ; and a back yoke insulator 284 disposed to cover a portion of the back yoke 281 . Insulator 284 is formed of an insulating material such as plastic.

The rotor is configured to include permanent magnets 270 .

The permanent magnet 270 may be mounted on the outer circumferential surface of the permanent magnet mounting part 224.

The permanent magnet mounting part 224 is provided to have a smaller diameter from the lower end of the first supporting part 223 to the axial lower part.

The permanent magnet 270 is provided to have a diameter smaller than the inner diameter of the stator core 280 .

The inner diameter of the stator core 280 represents the diameter of the circumference passing through the inner ends of the plurality of pole pieces in the circumferential direction.

The permanent magnet 270 and the first support part 223 may be provided to have the same diameter.

The permanent magnet 270 may be rotatably mounted on the permanent magnet mounting portion 224 of the rotating shaft member 220 with a radially inward air gap relative to the pole piece of the stator core 280 .

In order to limit the movement of the permanent magnet 270 in the axial direction, the end cap 271 may be installed on the underside of the permanent magnet mounting part 224 . End cap 271 may define a cylindrical shape having the same diameter as permanent magnet 270 .

One side of the permanent magnet 270 may be in contact with the first supporting part 223 having a diameter larger than that of the permanent magnet mounting part 224, thereby restricting movement in the axial direction upstream.

The end cap 271 is fixedly provided on the downstream side of the permanent magnet 270 .

The end cap 271 may be defined as a hollow cylinder to allow the permanent magnet mounting portion 224 to pass therethrough.

The other side of the permanent magnet 270 can be restricted from moving axially to the downstream side by the end cap 271 .

When three-phase alternating current is applied to each of the plurality of stator coils 283, the permanent magnet 270 may electromagnetically interact with the magnetic field generated around the stator coils 283 to generate a rotational force.

According to this configuration, the rotating shaft member 220 can rotate due to the electromagnetic interaction between the rotor and the stator.

The stator coil 283 and the stator core 280 are configured to exchange heat with air flowing along the inner passage 235 .

According to this configuration, the heat generated by the stator coil 283 and the stator core 280 can be cooled via heat exchange between the stator and the air.

The outer channel 243 may be provided between the second receiving portion 203 and the blade hub 240 .

The outer passage 243 may be defined as an axial straight line to minimize flow resistance.

Air can flow along two flow paths inside shroud 200. Viewed from the first flow path, air is sucked into the shroud 200 through the suction port 201 , and while flowing along the outer channel 243 through the suction channel and the expansion channel 242 , a part of the sucked air is discharged through the first discharge port 204 to the outside.

From the second flow path, another part of the sucked air flows from the expansion channel 242 into the internal channel 235 of the fan hub 240 through the plurality of communication holes 236 .

The air flowing along the inner channel 235 can cool the heat of the stator while exchanging heat with the stator coil 283, and then can be discharged to the outside through the second discharge outlet 237. Plural second row exits 237 It may be provided inside the lower end of the motor housing 230 .

The second bearing receiving portion 250 is provided at the lower end of the motor housing 230 .

The second bearing receiving portion 250 may be provided at an inner center portion of the motor housing 230 .

The second bearing receiving portion 250 may be defined as annular.

The second bearing mount may be received in the second bearing receiver 250 .

The second bearing may be embodied as a ball bearing 290 .

The second axial movement limiting portion 251 may extend radially inward from an upper end of the second bearing receiving portion 250 .

A through hole may be provided inside the second axial movement restricting portion 251 . The diameter of the through hole may be set larger than the diameters of the second support part 225 and the permanent magnet mounting part 224 .

The second axial movement limiting portion 251 may protrude radially inward and have an inner diameter smaller than the outer diameter of the second bearing. Therefore, the second bearing can limit axial movement of the permanent magnet mounting portion 224 when received in the second bearing receiving portion 250 .

The second bearing receiving portion 250 may be provided to be open downward.

The second buckle receiving groove 252 may be provided at the lower end of the second bearing receiving portion 250 to be recessed radially outward.

The second buckle 253 may be installed to be received in the second buckle receiving groove 252 .

The second buckle ring 253 can prevent the second bearing from being outwardly separated from the second bearing receiving portion 250 when received in the second buckle ring receiving groove 252 .

A plurality of second bridges 254 may be provided on the outer circumferential surface of the second bearing receiving portion 250 .

Each of the plurality of second bridges 254 is configured to project radially outward.

The outer circumference of the plurality of second bridges 254 may be disposed to contact the inner circumferential surface of the lower end of the motor housing 230 .

A plurality of second fastening holes 234 may be provided at the lower end of the motor housing 230 to pass through in the radial direction.

The plurality of second fastening holes 234 and the plurality of fastening parts 232 may be alternately spaced along the circumferential direction of the motor housing 230 .

A plurality of second fastening grooves 255 may be provided on the outer circumference of the plurality of second bridges 254 to respectively overlap with the plurality of second fastening holes 234 in the radial direction.

A plurality of fastening members such as screws can be respectively fastened to a plurality of second fastening grooves 255 through a plurality of second fastening holes 234 to install the second bearing receiving portion 250 on the motor housing through a plurality of second bridges 254 on the inner side of the body 230.

A plurality of second discharge outlets 237 may be provided between a plurality of second bridges 254 .

The plurality of second discharge ports 237 and the plurality of second bridges 254 may be alternately spaced in the circumferential direction inside the motor housing 230 .

A plurality of bus bars (not shown) may be disposed inside the lower end of the motor housing 230 . A plurality of bus bars may be provided in the second row outlet 237 .

A plurality of bus bars are respectively connected to the three-phase stator coil 283 to apply three-phase alternating current.

The first bearing receiving portion 226 can be integrally formed in the motor housing 230 by a plurality of first bridges 231, and the fan hub 240 and the motor housing 230 can be disposed to overlap each other in the radial direction and be joined to each other through adhesive, And the two are made of simple fastening structures, but can be firmly fastened to each other and arranged compactly to help reduce size and weight.

A plurality of fastening parts 232 may be provided to protrude from the outer circumferential surface of the motor housing 230, and the plurality of fastening parts 232 may be fastened to the lower end of the shield 200 by screws or the like, thereby further improving the connection between the shield 200 and the motor. The fastening force between the housings 230.

The plurality of fastening portions 232 and the plurality of second bridges 254 may preferably be disposed in a radial direction so as not to overlap each other outside and inside the motor housing 230 .

The plurality of fastening parts 232 and the plurality of second bridges 254 may be disposed respectively on the outside and inside of the motor housing 230 and spaced apart with different phase differences along the circumferential direction.

If the plurality of fastening portions 232 and the plurality of second bridges 254 are provided to overlap in the radial direction, the fastening members for fastening the shroud 200 and the motor housing 230 and the fastening members for fastening the motor housing 230 and the second bridge 254 are provided. The fastening members of the two bearing receiving portions 250 may be arranged to overlap each other in the radial direction, thereby making it difficult to fasten each fastening member to different parts respectively.

Therefore, the fastening position between the guard 200 and the fastening portion 232 of the motor housing 230 and the fastening position between the motor housing 230 and the second bridge 254 of the second bearing receiving portion 250 can be set to are spaced apart from each other in the circumferential direction to have different phase angles, thereby ensuring miniaturization and assembleability of the motor despite the small assembly space.

Referring to Figures 10 and 11, the first bearing supporting the first support portion 223 may be implemented as a hollow Air bearing 260.

Air bearing 260 may be defined as a hollow cylinder. The shaft receiving portion is provided inside the air bearing 260 .

The air bearing 260 is provided to form an air gap between the outer circumferential surface of the first support part 223 and the inner circumferential surface of the air bearing 260 .

The air gap can be 0.04mm or less.

In order to ensure the assembleability of the rotating shaft member 220 and the rotor, the inner diameter of the air bearing 260 may be set smaller than the inner diameter of the stator core 280 .

The inner diameter of the stator core 280 represents the diameter of a circle passing through the inner ends of the plurality of teeth 282 in the circumferential direction.

The inner diameter (d) of the air bearing 260 may be set larger than the length (height) of the air bearing 260 to reduce wear of the inner diameter surface of the air bearing 260.

The ratio of the length (L) of the air bearing 260 to the inner diameter (d) of the air bearing 260 may be 0.7 or less. When the length/inner diameter (L/d) ratio of the air bearing 260 exceeds 0.7, the amount of wear on the inner diameter surface of the air bearing 260 may increase significantly.

Since the air bearing 260 rotatably supports the rotating shaft member 220 in a non-lubricated state, a material having a low friction coefficient and excellent wear resistance is used.

For example, air bearing 260 may be made from polyetheretherketone (PEEK) or polyaryletherketone (PAEK) materials that have excellent non-lubricating friction characteristics and wear resistance.

PEEK or PAEK will cause little wear on the bearings after operation, and the gap between the PEEK and the shaft will change very little.

The air bearing 260 can form an air layer between the rotating shaft 220 and the inner circumferential surface of the air bearing 260, and support the rotating shaft 220 in a non-contact manner without additional working fluid such as lubricating oil.

At least one first O-ring 262 may be mounted on the outer circumferential surface of the first bearing. In this embodiment, a configuration is shown with one first O-ring 262 installed.

Air bearing 260 may be received in first bearing receiver 226 .

The first O-ring mounting groove 261 may be radially recessed on the outer circumferential surface of the air bearing 260 in the circumferential direction.

The first O-ring 262 may be installed to be received in the first O-ring mounting groove 261 .

The plurality of first O-rings 262 are made of elastic materials such as rubber.

A plurality of first O-ring mounting grooves 261 may be provided to be spaced apart along the length direction (axial direction) of the air bearing 260 .

The plurality of first O-rings 262 are in close contact with the first bearing receiving portion 226 .

According to this configuration, the plurality of first O-rings 262 may be aligned on the same centerline for concentricity between the air bearing 260 and the first bearing receiver 226 . A plurality of first O-rings 262 may prevent the air bearing 260 from rotating in the first bearing receiver 226 .

The plurality of first O-rings 262 can reduce vibration and impact transmitted to the air bearing 260 from the outside.

The second bearing supporting the second support part 225 may be implemented as a ball bearing 290 .

The O-ring bracket 291 may be installed on the outer circumferential surface of the ball bearing 290 to surround the ball bearing 290 .

A plurality of second O-ring mounting grooves 292 may be provided on the outer circumferential surface of the O-ring bracket 291 . In this embodiment, a configuration in which two second O-ring mounting grooves 292 are provided is shown.

The plurality of second O-rings 293 may be installed in the plurality of second O-ring installation grooves 292 respectively.

The plurality of second O-rings 293 may be aligned on the same centerline for concentricity between the ball bearing 290 and the second bearing receiver 250 . The plurality of second O-rings 293 can prevent the ball bearing 290 from rotating relative to the second bearing receiving portion 250 .

The plurality of second O-rings 293 are made of elastic materials such as rubber.

The plurality of second O-rings 293 can reduce vibration and impact transmitted to the ball bearing 290 from the outside.

Therefore, according to the present invention, the air bearing 260 serves as a first bearing that supports the first supporting portion 223 of the rotating shaft member 220 adjacent to the impeller 210 .

Since the air bearing 260 is lubricated by air and does not require additional working fluid, no friction occurs between the air bearing 260 and the rotating shaft 220 .

Therefore, even when the rotating shaft 220 rotates at a high speed higher than 100,000 rpm, wear due to friction between the air bearing 260 and the rotating shaft 220 will not occur, thereby extending the life of the bearing. In addition, an air bearing 260 can be applied to extend the life of the fan motor rotating at high speed.

Additionally, the air bearing 260 may have the advantage of extending its life even as its diameter increases.

Therefore, the diameter of the air bearing 260 may be increased to increase the axial diameter of the first support part 223.

In addition, the diameter (thickness) of the first support portion 223 of the rotating shaft member 220 adjacent to the impeller 210 may be increased (thickened) to prevent the rotating shaft member 220 from bending due to uneven load on the impeller 210 during high-speed rotation. In addition, the thickness of the first supporting part 223 may be increased to increase the limit speed allowed by the rotating shaft 220 .

For example, the diameter of the first supporting part 223 may be set larger than the diameter of the impeller coupling part 221 of the rotating shaft member 220 coupled with the impeller 210 .

In addition, the diameter of the first support portion 223 may be set larger than the diameter of the permanent magnet mounting portion 224 of the rotation shaft member 220 on which the permanent magnet 270 is mounted.

In addition, the diameter of the first support part 223 may be set larger than the diameter of the second support part 225 supported by the second bearing.

After the stator is preassembled inside the shroud 200 , the rotating shaft member 220 passes through the rotor receiving hole formed inside the stator core 280 to be received in the first receiving portion 202 and the second receiving portion 203 of the shroud 200 . The rotating shaft member 220 is assembled so as to be disposed on the same center line of the second receiving portion 203 .

In order to couple the first supporting part 223 to the inner circumferential surface of the first bearing through the rotor receiving hole, the diameter of the first supporting part 223 may preferably be set smaller than the inner diameter of the stator core 280 .

In addition, the inner diameter of the air bearing 260 may be set smaller than the inner diameter of the stator core 280 to ensure the assemblability of the rotating shaft member 220 and the like.

For example, when the ball bearing 290 is coupled to the second supporting part 225 , the first supporting part 223 of the rotating shaft 220 may be assembled to the inner side of the air bearing 260 .

In addition, the air bearing 260 may not be provided in the suction channel, the expansion channel 242 and the external channel 243 which are the main channels of the fan motor, and the impeller 210 may be provided to cover the first bearing receiving portion 226 accommodating the air bearing 260, thereby blocking Foreign matter such as dust enters the air bearing 260 .

In addition, the first O-ring mounting groove 261 may be provided on the outer wall of the air bearing 260, and the first O-ring 262 may be installed in the first O-ring mounting groove 261, thereby allowing the rotating shaft 220 to axially align The centerline of the quasi-shield 200.

In addition, the first O-ring 262 may be formed of an elastic material, thereby reducing impact transmitted to the air bearing 260 from the outside.

At the same time, the ball bearing 290 can serve as a second bearing that supports the rotating shaft The second support portion 225 of the member 220 is located on the opposite side of the impeller 210 relative to the permanent magnet mounting portion 224 .

Since the second support portion 225 of the rotating shaft member 220 located on the opposite side of the impeller 210 is less affected by the uneven load of the impeller 210 , the shaft diameter of the second support portion 225 may be smaller than the shaft diameter of the first support portion 223 .

Therefore, the ball bearing 290 may be applied to the second support part 225. Ball bearing 290 is cheaper than air bearing 260. Therefore, in terms of cost, it is more advantageous to use one air bearing 260 and one ball bearing 290 than to use two air bearings 260 to support both sides of the rotating shaft 220 .

In addition, when only the air bearing 260 is used for two bearings, a thrust bearing should be used, which is a necessary component. However, by using an air bearing 260 and a ball bearing 290, the thrust bearing can be removed, thereby significantly reducing the size and weight of the fan motor.

In addition, the fan hub 240 and the motor housing 230 may be disposed on a straight line with each other on the downstream side of the impeller 210 with respect to the airflow direction generated by the impeller 210, and be disposed between the shroud 200, the fan hub 240 and the motor housing 230. The external channels 243 between them can be arranged in a straight line without bending, thereby minimizing the flow resistance of the air and improving the cooling efficiency of the air to the motor.

In addition, the plurality of fan blades 241 protruding from the outer circumferential surface of the fan hub 240 can be coupled to the inner circumferential surface of the shroud 200 in a force-fitting manner, thereby allowing the shroud 200 and the fan hub 240 to be firmly tightened with each other. solid.

The first bearing receiving portion 226 and the motor housing 230 may be integrated by a plurality of first bridges 231 .

The fan hub 240 and the motor housing 230 may be disposed to overlap in a radial direction and be joined to each other through an adhesive, thereby being firmly fastened to each other.

The plurality of fastening parts 232 may protrude radially outward from the outer circumferential surface of the motor housing 230, and the plurality of fastening parts 232 may be fastened to the inner circumferential surface of the shield 200 by screws or the like, thereby allowing the shield 200 to and motor housing 230 are firmly coupled to each other.

The second bearing receiving part 250 and the motor housing 230 may be connected to each other through a plurality of second bridges 254, and the motor housing 230 and the second bridge 254 may be connected to each other through fastening members such as screws, thereby utilizing a simple and compact Fastening structure greatly reduces the size and weight of the motor.

Furthermore, the fastening positions between the guard 200 and the fastening portion 232 of the motor housing 230 and the fastening positions between the motor housing 230 and the second bridge 254 of the second bearing receiving portion 250 may be provided as are spaced apart from each other in the circumferential direction to have different phase angles so that despite the small assembly space This ensures miniaturization and assembleability of the motor.

FIG. 12 is a perspective view showing the first O-ring mounting groove 261' on the air bearing 260' according to another embodiment of the present invention.

FIG. 13 is a cross-sectional view taken along line XIII-XIII in FIG. 12 , which shows the arrangement of a plurality of first O-rings 262' installed on the first O-ring mounting groove 261' of the air bearing 260'.

The difference between this embodiment and the aforementioned embodiments of FIGS. 7 to 11 is that a plurality of first O-ring mounting grooves 261' are provided on the outer circumferential surface of the air bearing 260' along the circumferential direction.

A plurality of first O-ring mounting grooves 261' are provided spaced apart along the length direction (axial direction) of the air bearing 260'. A plurality of first O-rings 262' may be installed to be received in a plurality of first O-ring installation grooves 261' respectively.

Other components are the same as or similar to those of the embodiment of FIGS. 7 to 11 , and therefore redundant description thereof will be omitted.

FIG. 14 is an exploded perspective view of a fan motor according to yet another embodiment of the present invention.

FIG. 15 is a perspective view showing the bearing part and the bracket part shown in FIG. 14 .

FIG. 16 is a perspective view showing the sealing portion shown in FIG. 14 .

17 to 22 are views showing other examples of the sealing portion shown in FIG. 16 .

FIG. 23 is a cross-sectional view showing the arrangement of the fan motor shown in FIG. 14 in an assembled state.

FIG. 24 is a partial enlarged view of the fan motor showing the periphery of the bearing portion shown in FIG. 23 .

FIG. 25 is a view showing the internal space of the housing part except the bearing part and the retaining ring shown in FIG. 24 .

FIG. 26 is a conceptual diagram showing an enlarged portion of the fan motor around the bearing portion shown in FIG. 24 .

Referring to FIGS. 14 to 26 , the fan motor 300 includes a rotating shaft 310 , a bearing part 320 , and a sealing part 330 .

The rotation shaft 310 may be configured to extend in one direction and be coupled to the rotor 352 so as to rotate together in one direction when the rotor 352 rotates.

The rotating shaft 310 may be configured to rotate about a central axis 310a along which It is defined along the length direction (D1) of the rotating shaft 310.

Meanwhile, the radial direction (D2) of the rotating shaft member 310 may be defined as a direction perpendicular to the length direction (D1) of the rotating shaft member 310.

The rotor 352 may be provided inside the stator 351. In addition, the rotor 352 may be configured to rotate in one direction through the rotating magnetic field generated by the stator 351 .

The rotor 352 may include a magnet portion 352a disposed to surround a portion of the rotation shaft 310 and an end cap 352b disposed at one end of the magnet portion 352a. The magnet portion 352a may be configured to have magnetism.

The stator 351 may include a stator core 351a, a stator coil 351b, and an insulator 351c.

A plurality of stator coils 351b may be provided and may be wound around the stator core 351a.

In addition, the insulator 351c may be provided between the stator core 351a and the stator coil 351b to electrically insulate the stator core 351a and the stator coil 351b.

Meanwhile, the impeller 371 may be coupled and fixed to one end of the rotating shaft member 310.

The impeller 371 may include: a hub 371a constituting a main body of the impeller 371; and a plurality of blades 371b protruding from the outer surface of the hub 371a along the circumference of the hub 371a. A through hole 371c through which one end of the rotating shaft member 310 is inserted may be provided in the hub 371a.

Impeller 371 may generate airflow during rotation. Additionally, fan motor 300 may include fan blades 372 that guide the airflow generated by impeller 371. The fan blades 372 may be arranged on the fan blade body 372a along the circumference of the fan blade body 372a.

The impeller 371 and the fan blades 372 may be arranged to be surrounded by a shroud 380 . The shroud 380 may be configured to define the appearance of the fan motor 300 .

An opening 380a may be provided on a side of the shroud 380 adjacent to the impeller 371 to allow air to flow into the impeller 371 from the outside.

On the other hand, a ball bearing 361 may be provided on the other side of the rotating shaft member 310. The ball bearing 361 supports the dead weight of the rotating shaft member 310 and the force exerted on the rotating shaft member 310 when the rotating shaft member 310 and the bearing portion 320 are fixed together at a predetermined position. The load on the rotating shaft 310.

The bearing portion 320 and the ball bearing 361 may be provided to surround different portions of the rotating shaft 310 respectively.

Ball bearing 361 can be equipped with a rolling bearing. Fan motor 300 may include A ball bearing housing 365 is provided to surround the ball bearing 361 to accommodate the ball bearing 361 .

Additionally, a ball bearing bracket 362 is provided to surround the ball bearing 361 and may be provided between the ball bearing 361 and the ball bearing housing 365 .

In addition, a ball bearing O-ring 362a may be disposed between the ball bearing bracket 362 and the ball bearing housing 365 to seal the gap between the ball bearing bracket 362 and the ball bearing housing 365. A plurality of ball bearing O-rings 362a may be provided.

In addition, a ball bearing retaining ring 363 configured to support the ball bearing 361 and/or the ball bearing bracket 362 when coupled to the ball bearing housing 365 may be provided at one side of the ball bearing 361 along the length direction (D1) of the rotating shaft 310 side. The ball bearing retaining ring 363 may function to prevent the rotating shaft member 310 and the ball bearing 361 from being separated to the outside.

The bearing part 320 and the sealing part 330 included in the fan motor 300 will be described below.

The bearing portion 320 is provided to surround a portion of the rotation shaft 310 . For example, the bearing portion 320 may be disposed relatively closer to the impeller 371 than the ball bearing 361 .

One surface of the bearing portion 320 facing the rotating shaft member 310 may be spaced apart from the rotating shaft member 310 by a predetermined distance to define a gap 320a through which air (a) flows.

In this specification, the bearing part 320 may be called an air bearing.

Here, the air (a) may include foreign matter such as dust. In addition, foreign matter such as dust may be moved or floated by the airflow generated during operation of the fan motor 300 to flow into the gap 320a.

Unlike the ball bearing 361 , the bearing portion 320 is configured to support the rotating shaft 310 by air (a) flowing through the gap 320 a defined between the rotating shaft 310 and the bearing portion 320 . In this way, the bearing portion 320 has a structure in which the operating area of the bearing portion 320 is open. In addition, the distance defined in the gap 320a between the rotating shaft member 310 and the bearing portion 320 may be approximately 40 microns.

In addition, as shown in FIG. 26 , the airflow caused by air (a) entering and exiting the gap 320a may include a first airflow (a1) generated from the gap 320a to the outside of the gap 320a; and flowing into the gap from an external area of the gap 320a. Second air flow (a2) in 320a.

Meanwhile, the fan motor 300 may further include a housing part 340 provided with an inner space 340a accommodating the bearing part 320.

In addition, the housing part 340 may include a groove part 341 defined as a depression on one surface facing the rotation shaft member 310 to accommodate and secure the sealing part 330 on one side.

The housing part 340 may include a bracket part 321 disposed to surround the outer circumference of the bearing part 320 to accommodate the bearing part 320 .

An O-ring 321b provided to seal the gap between the bracket part 321 and the housing part 340 may be provided between the bracket part 321 and the housing part 340.

The O-ring 321b may be made of rubber material, and may be provided in plural numbers. An O-ring groove 321a may be provided on the outer surface of the bracket part 321, and the O-ring 321b is insertably fixed to the O-ring groove 321a.

The number of O-ring grooves 321a may be set to correspond to the number of O-rings 321b. In the drawings of the present invention, the case where two O-ring grooves 321a and O-rings 321b are respectively applied is shown.

In addition, the retaining ring 322 configured to support the bearing part 320 and/or the bracket part 321 when coupled to the housing part 340 may be provided on one side of the bearing part 320 along the length direction (D1) of the rotating shaft member 310.

The housing portion 340 may include a buckle groove 342 in which a portion of one side of the buckle 322 is configured to be received. Additionally, the buckle 322 may be made of metal material.

Additionally, the buckle 322 may be defined as having a circular ring shape. The retaining ring 322 may function to prevent the rotating shaft member 310 and the bearing portion 320 from being separated from the housing portion 340 .

The sealing portion 330 may be provided adjacent to the bearing portion 320 in the length direction (D1) of the rotating shaft 310 and configured to form a passage for air (a) entering and exiting the gap 320a provided between the rotating shaft 310 and the bearing portion 320. part of the flow path.

In addition, the sealing portion 330 is provided to block a portion of the air (a) flowing toward the gap 320a along the circumference of the rotating shaft member 310.

The sealing portion 330 may be configured to include at least one of polytetrafluoroethylene (PTFE) and rubber. PTFE can be made from DuPont's Teflon as a fluororesin.

Referring to FIG. 16 , the sealing portion 330 may be defined as having a circular ring shape. Furthermore, as shown in FIGS. 17 and 18 , the sealing unit 330 may include a crack 331 .

The slit 331 may be disposed to pass through in a direction perpendicular to one surface facing the bearing portion 320 . The cracks 331 may form part of the flow path of air (a).

As shown in FIG. 17 , the sealing portion 330 may be defined as having a C-shape provided with a slit 331 .

Additionally, as shown in Figure 18, the crack 331 may be defined to have a hole shape. A plurality of hole-shaped cracks 331 may be provided.

An example of the fan motor 300 using the sealing portion 330 having the crack 331 will be described below with reference to other drawings of the present invention.

Meanwhile, as shown in FIG. 19 , the sealing part 330 may further include a mesh part 332.

The mesh part 332 may be provided on the slit 331 provided in the sealing part 330 to divide the flow path of the air (a) into a plurality of areas.

The mesh portion 332 may be made of the same type of material as the sealing portion 330 , or may be made of a different type of material than the sealing portion 330 .

According to the configuration of the mesh portion 332 described above, a portion of the air (a) flowing into the gap 320 a through the cracks 331 can collide with the mesh portion 332 .

Therefore, the possibility that foreign matter such as dust in the air (a) flows into the gap 320a can be further reduced.

Meanwhile, referring to FIG. 20 , the sealing part 330 may include a first part 330a and a second part 330b.

FIG. 20(a) is a conceptual view of the sealing portion 330 viewed from the top; and FIG. 20(b) is a cross-sectional view taken along line XX-XX shown in FIG. 20(a).

The first portion 330a may form part of the sealing portion 330 and may be made of the first material.

The second portion 330b may constitute another portion of the sealing portion 330 and may be made of a second material different from the first material.

For example, the first portion 330a may be disposed to surround at least a portion of the second portion 330b, and the second material may be stiffer than the first material.

For example, the first material may be made of any one of PTFE (polytetrafluoroethylene) and rubber, and the second material may be made of a metal material.

The first part 330a and the second part 330b may be made by double injection molding. Where the type of first material and/or second material is metal, a metallic material in powder form may be used during molding of the first part 330a and the second part 330b.

Furthermore, as shown in FIG. 21 , the sealing part 330 may include: a first part 330 constituting one side of the sealing part 330 formed of a first material; and a second part 330b formed of a second material different from the first material.

Here, the first portion 330 a constituting one side of the sealing portion 330 may be configured to be received in the groove portion 341 of the housing portion 340 . In addition, the second portion 330b constituting the other side of the sealing portion 330 may define Part of the flow path of air (a).

For example, the first material constituting the first part 330a may be made of a material with excellent properties to be fixed on the groove part 341 of the housing part 340, and the second material constituting the second part 330b may be made of a material with relatively low The air (a) flow resistance is made of materials.

In other words, while the second portion 330b allows air (a) to flow in and out of the gap 320a to flow more efficiently, the first portion 330a of the sealing portion 330 can more stably maintain a state of being fixed to the housing portion 340, thereby being more stable Provide the performance of the bearing portion 320 effectively.

Furthermore, as shown in FIG. 22 , the sealing portion 330 may include a bent portion 333 . FIG. 22(a) is a conceptual view of the sealing portion 330 viewed from the top; and FIG. 22(b) is a cross-sectional view taken along line XXII-XXII shown in FIG. 22(a).

The curved portion 333 may be provided on the other side of the sealing portion 330 forming part of the flow path of the air (a) and configured to define a curved surface toward an outer region of the gap 320a in the length direction (D1) of the rotating shaft member.

In other words, the bend 333 may be defined in the air (a) entering and exiting the gap 320a along the first airflow (a1) generated from the gap 320a toward the outside of the gap 320a.

An example of the fan motor 300 applying the sealing portion 330 having the bent portion 333 will be described below with reference to other drawings of the present invention.

Meanwhile, referring to FIG. 26 , the sealing part 330 may extend from the housing part 340 toward the rotating shaft member 310 . In other words, the sealing portion 330 may be provided to extend in the radial direction (D2) of the rotating shaft member 310 in the housing portion 340 .

In addition, one side of the sealing part 330 may be fixed to the housing part 340. In FIG. 26 , a configuration is shown in which one side of the sealing portion 330 is fixed and accommodated in the groove portion 341 , but one side of the sealing portion 330 may be provided to extend from one surface of the housing portion 340 .

In addition, the other side of the sealing portion 330 may be spaced apart from the rotating shaft member 310 by a predetermined distance to form a part of the flow path of the air (a).

In addition, the sealing portion 330 may be provided above the bearing portion 320 or below the bearing portion 320 in the longitudinal direction (D1) of the rotating shaft 310 . In FIG. 26 , the arrangement in which the sealing part 330 is provided below the bearing part 330 is shown.

Furthermore, referring to FIG. 26 , the gap formed between the rotating shaft member 310 and the sealing portion 330 and the gap formed between the rotating shaft member 310 and the bearing portion 320 may be different from each other.

In particular, the first gap (g1) is formed between the rotating shaft member 310 and the other side of the sealing portion 330 facing the rotating shaft member 310, and the second gap (g2) is formed between the rotating shaft member 310 and the bearing portion 320 facing the rotating shaft. Between one surface of the member 310, the first gap (g1) may be defined to be narrower than the second gap (g2).

For example, the first gap and the second gap (g1, g2) may be formed to satisfy the relationship "g1=g2/2".

Accordingly, the sealing portion 330 may be provided with a first gap (g1) defined smaller than the second gap (g2) to provide a minimum gap for the flow of air (a) required for the normal operation of the bearing portion 320, such as the first air flow (a1), while trying to block the flow of air, such as the second airflow (a2), into the gap 320a, thereby preventing foreign matter such as dust from entering the gap 320a.

Other examples of the fan motor 300 shown in FIG. 26 will be described below with further reference to FIGS. 27-34 and 14-26.

27 to 34 are conceptual diagrams showing other examples of the fan motor 300 shown in FIG. 26 .

First, referring to FIG. 27 , the sealing portions 330 may be provided in plural numbers, and may include an upper sealing member 335a and a lower sealing member 335b. The upper sealing member 335a and the lower sealing member 335b may be made of the same material or may be made of different materials.

The upper sealing member 335a may be provided on the upper side of the bearing portion 320 in the length direction (D1) of the rotating shaft 310. One side of the upper sealing member 335a may be disposed below the buckle 322 and may be received with the buckle 322 in and coupled to a buckle groove 342 provided within the housing portion 340 .

The lower sealing member 335b may be provided below the bearing portion 320 in the longitudinal direction (D1) of the rotating shaft 310. One side of the lower sealing member 335b may be received and fixed in a groove portion 341 provided within the housing portion 340.

Among the air (a) entering and exiting the gap 320a, the second airflow (a2) flowing into the gap 320a from the outer area of the gap 320a may be formed not only below the bearing part 320, but also above the bearing part 320.

According to the configuration of the upper sealing member 335a and the lower sealing member 335b, it may be configured to block a part of the second airflow (a2) generated in the direction of the inflow gap 320a above and below the bearing portion 320, thereby minimizing the amount of air contained in the second airflow (a2). Foreign matter such as dust in the second air flow (a2) flows into the gap 320a, and the gap 320a is formed between the bearing portion 320 and the rotating shaft member 310.

Next, referring to Figure 28, one side of the sealing portion 330 may be fixed to the housing portion 340, The other side of the sealing portion 330 can be accommodated in one side of the rotating shaft member 310 . The rotating shaft 310 may include a shaft groove 311 defined to be recessed on one surface of the rotating shaft 310 to accommodate the other side of the seal 330 .

In addition, one side of the sealing part 330 may be fixed while being accommodated in the groove part 341 provided on the housing part 340.

Here, as shown in FIGS. 17 and 18 , the sealing part 330 may include a slit 331 disposed to pass through in a direction perpendicular to one surface facing the bearing part 320 to form a part of the flow path of the air (a).

In other words, the sealing portion 330 may be provided to extend in the radial direction (D2) of the rotating shaft 310 , and the crack 331 may be provided on the sealing portion 330 to pass through in the lengthwise direction (D1) of the rotating shaft 310 .

Here, air (a) entering and exiting the gap 320a formed between the bearing part 320 and the rotating shaft member 310 may be blocked by the sealing part 330 without the crack 331.

In other words, air entering and exiting gap 320a may flow through slit 331. In addition, in the air (a), the second airflow (a2) generated in the direction of flowing into the gap 320a may be blocked by the remaining portion of the sealing portion 330 without the crack 331.

In addition, in the case where the sealing portion 330 is provided with the slit 331 and is defined in a C shape, it can be deformed more easily than an annular sealing portion 330 , thereby improving the assembly of the sealing portion 330 into the groove portion 341 or the shaft recess. The operating efficiency of the process of tank 311.

In addition, in the case where the sealing portion 330 is provided with the slit 331 defined to have a hole shape, compared to the sealing portion 330 having a C-shape, groove portions on one side and the other side of the sealing portion 330 are respectively accommodated therein. The area occupied by the hollow space 341 or the shaft groove 311 can be very small, thereby maintaining the coupling state of the sealing portion 330 to the groove portion 341 or the shaft groove 311 more stably.

On the other hand, although not shown in FIG. 28 , as described above, the mesh portion 332 divides the flow path of the air (a) into a plurality of areas and may be provided on the slit 331 of the sealing portion 330 .

Next, referring to FIG. 29 , one side of the sealing part 330 may be fixed to the rotating shaft 310 , and the other side of the sealing part 330 may extend in a direction away from the rotating shaft 310 .

In addition, the rotating shaft 310 may include a shaft groove 311 defined as a depression on one surface of the rotating shaft 310 to secure one side of the sealing portion 330 while accommodating it. In addition, as shown in FIG. 29 , the other side of the sealing portion 330 may be configured to form a gap for air (a) entering and exiting the gap 320a. part of the flow path.

Furthermore, the sealing portion 330 may be made of the same type of material as the rotating shaft member 310 . For example, when the rotating shaft member 310 is made of a metal material, the sealing portion 330 may be made of the same type of metal material as the rotating shaft member 310 .

Therefore, even when the high-speed rotation of the rotating shaft member 310 and the sealing portion 330 causes adhesion to each other, the operation of the bearing portion 320 and the function of the sealing portion can be performed normally.

Next, referring to FIG. 30 , the sealing portion 330 may be provided above or below the bearing portion 320 in the length direction (D1) of the rotating shaft 310 .

In the case of the sealing portion 330 shown in FIG. 30 , the sealing portion 330 is shown to be provided below the bearing portion 320 .

In addition, the sealing parts 330 may be provided in plural numbers, and may be composed of a first sealing member 336a and a second sealing member 336b. In addition, the first sealing member 336a may be disposed closer to the bearing portion 320 than the second sealing member 336b in the length direction (D1) of the rotating shaft 310.

In Figure 30, the first sealing member 336a and the second sealing member 336b are shown disposed below the bearing portion 320, but may be disposed above the bearing portion 320 instead of below it.

Here, the first sealing gap 336a1 is formed between the rotating shaft 310 and the other side of the first sealing member 336a facing the rotating shaft 310, and the second sealing gap 336b1 is formed between the rotating shaft 310 and the second sealing member 336b. Between the other sides facing the rotating shaft member 310, the first sealing gap 336a1 and the second sealing gap 336b1 may be formed to be the same.

One side of the first sealing member 336a and the second sealing member 336b may be fixed while being received in the first and second grooves 341a and 341b respectively defined to be recessed on one surface of the housing part 340.

The lengths of the first sealing member 336a and the second sealing member 336b in the radial direction (D2) of the rotation shaft 310 may be defined to be different from each other.

At this time, the first groove 341a and the second groove 341b may be provided to have different depths recessed on one surface of the housing part 340, so that the first sealing gap 336a1 and the second sealing gap 336b1 are formed to be the same.

According to the configuration of the first sealing member 336a and the second sealing member 336b, in the air (a) entering and exiting the gap 320a, the area that blocks the second airflow (a2) generated in the direction of flowing into the gap 320a can be increased to minimize Foreign matter such as dust contained in the second airflow (a2) flows into the gap Possibilities in 320a.

Next, referring to FIG. 31 , similar to the fan motor 300 shown in FIG. 30 , a plurality of sealing parts 330 may be provided to include a first sealing member 336a and a second sealing member 336b.

Here, in the case of the first sealing member 336a and the second sealing member 336b shown in FIG. 31 , the first sealing gap 336a1 is formed on the other side of the rotating shaft 310 and the first sealing member 336a facing the rotating shaft 310 A second sealing gap 336b1 is formed between the rotating shaft 310 and the other side of the second sealing member 336b facing the rotating shaft 310. The first sealing gap 336a1 and the second sealing gap 336b1 may be formed to be different from each other.

For example, as shown in FIG. 31 , the second seal gap 336b1 may be formed smaller than the first seal gap 336a1.

According to the above-described configuration of the first sealing member 336a and the second sealing member 336b, the second sealing member 336b is disposed in the first sealing member 336a relative to the flow of the second airflow (a2) in the air (a) in the inlet and outlet gap 320a. On the upstream side of the direction, the first airflow (a1) generated from the gap 320a to the outer area of the gap 320a can be effectively maximized while minimizing the second airflow (a2) flowing into the area in the gap 320a, thereby more stably The operation of the bearing portion 320 is provided.

In other words, the first sealing gap 336a1 may be formed relatively larger than the second sealing gap 336b1, thereby reducing an area that blocks the first airflow (a1) in the first sealing member 336a and the second sealing member 336b.

Next, referring to FIG. 32 , the groove portion 341 provided in the housing portion 340 may be provided to be inclined toward the outer area of the gap 320 a in the length direction (D1) of the rotation shaft member 310 .

Here, one side of the sealing portion 330 may be accommodated in the groove portion 341 of the housing portion 340 to extend obliquely toward the outer area of the gap 320a in the length direction (D1) of the rotating shaft member 310.

According to the configuration of the groove portion 341 and the sealing portion 330 described above, the other side of the sealing portion 330 forming the air (a) flow path may be provided to face the outer area of the gap 320a so as to face the air (a) in and out of the gap 320a. The first airflow (a1) generated in the outer area of the gap 320a flows more efficiently, thereby allowing the bearing portion 320 to operate more stably.

In addition, when foreign matter such as dust flows into the gap 320a, the foreign matter such as dust can be discharged to the outer area of the gap 320a again faster by the first airflow (a1).

On the other hand, in the case where the second airflow (a2) is generated toward the gap 320a, the sealing portion 330 may be defined to be inclined in the opposite direction to the second airflow (a2) to further increase the resistance to the second airflow (a2). The resistance of the flow (a2) is further reduced, thereby further reducing the possibility that the second airflow (a2) flows into the gap 320a.

In other words, due to the configuration of the sealing portion 330, the phenomenon that foreign matter such as dust flows into the gap 320a together with the second airflow (a2) can be minimized.

Next, referring to FIG. 33 , the sealing portions 330 may be provided in plural numbers, and may include a housing sealing member 337a and a shaft sealing member 337b.

The housing sealing member 337a may be provided to extend from the housing part 340 toward the rotating shaft 310, and one side of the housing sealing member 337a may be fixed to the housing part 340, while the other side of the housing sealing member 337a may be connected to the rotating shaft 310. The shaft members 310 are spaced apart by a predetermined distance. One side of the housing sealing member 337a may be fixed while being accommodated in the groove portion 341 provided in the housing portion 340.

One side of the shaft sealing member 337b may be fixed to the rotating shaft 310, and the other side thereof may extend in a direction away from the rotating shaft 310.

Additionally, shaft seal member 337b may be configured to form a portion of the flow path of air (a) into and out of gap 320a with housing seal member 337a. One side of the shaft sealing member 337b may be fixed while being received in a shaft groove 311 provided in the rotating shaft 310.

In this way, the housing sealing member 337a and the shaft sealing member 337b may be alternately provided on the right side and the left side, respectively, in the length direction (D1) of the rotating shaft 310.

Therefore, the diagram shows the following flow: the second air flow (a2) generated towards the gap 320a in the air (a) entering and exiting the gap 320a will first pass through the other side of the shaft sealing member 337b and then pass through the housing sealing member. The other side of 337a.

Here, the other side of the housing sealing member 337a and the other side of the shaft sealing member 337b forming a part of the flow path of the air (a) may be provided alternately with each other, so that the second airflow ( a2) More difficult to flow.

In other words, due to the configurations of the housing sealing member 337a and the shaft sealing member 337b, the possibility of foreign matter such as dust flowing into the gap 320a together with the second airflow (a2) can be greatly reduced.

Finally, referring to FIG. 34 , the other side of the sealing portion 330 may form a part of the flow path of air (a) in and out of the gap 320 a formed between the bearing portion 320 and the rotating shaft member 310 .

Here, the sealing part 330 may include a bent part 333.

As shown in FIG. 22 , the bent portion 333 may be provided on the other side (inside) of the sealing portion 330 that forms the flow path of the air (a) so as to be formed in the length direction (D1) of the rotating shaft member 310 Curved surface towards the outer area of gap 320a.

According to the above-described configuration of the sealing portion 330 having the curved portion 333, the flow of the first airflow (a1) generated toward the outer area of the gap 320a in the air (a) entering and exiting the gap 320a can be performed more efficiently along the curved portion 333. .

In other words, a part of the air (a) flowing to the gap 320a may be blocked by the sealing part 330 to prevent foreign matter such as dust from flowing into the gap 320a, and the flow of the air (a) flowing through the gap 320a may be formed more stably to prevent The reliability of the operation of the bearing part 320 is further improved.

101:Suction port

103:Extended channel

105: Cooling channel

106:Discharge outlet

111: Impeller coupling part

112: First support part

113:Permanent magnet mounting department

114: Second support part

120: Impeller

121:wheel hub

122:Blade

132:Back yoke

133: Teeth

134:Stator coil

136:Bus

137:Insulator

140:Rotor

141:Permanent magnet

150:First bearing housing

151: First bearing receiving part

152: First axial movement restriction part

153:First buckle receiving slot

160:First fan impeller hub

161:First fan blade

163:Second fan impeller hub

164:Second fan blade

170: Second bearing housing

171: Second bearing receiving part

172:Bridge

173: Second axial movement restriction part

174:Second buckle receiving slot

180:Air bearing

181: First O-ring bracket

183:First O-ring

190:Ball bearing

191: Second O-ring bracket

192:Second O-ring installation groove

193:Second O-ring

Claims (17)

A fan motor includes: a shield, an upstream end and a downstream end in an air flow direction respectively have a suction port and a first discharge port; a rotating shaft rotatably arranged on the shield The interior of the cover is provided with a first support part and a second support part spaced apart from each other in the axial direction, and a permanent magnet mounting part provided between the first support part and the second support part; An impeller is disposed at one end of the rotating shaft; an air bearing is disposed adjacent to the impeller and lubricated with air, and has an air gap between it and the first support portion to rotatably support the first support part; a permanent magnet, installed on the permanent magnet mounting part; a ball bearing, disposed at the other end of the rotating shaft and the side opposite to the first support part, and the permanent magnet is between the ball bearing and the third support part. between a supporting part to rotatably support the second supporting part; a first O-ring bracket installed on an outer circumferential surface of the air bearing to surround the air bearing; a plurality of first O-rings , respectively installed in a plurality of first O-ring mounting grooves provided in the first O-ring bracket; a second O-ring bracket is installed to surround the ball bearing, and is provided with a plurality of a second O-ring installation groove; and a plurality of second O-rings respectively installed in the plurality of second O-ring installation grooves. The fan motor of claim 1, wherein the air bearing is made of PAEK (polyaryl ether ketone) or PEEK (polyether ether ketone) material. The fan motor of claim 1, wherein a plurality of first O-ring mounting grooves are spaced apart along the length direction of the air bearing, and a plurality of first O-rings are respectively installed on the first O-rings. Ring installation groove. The fan motor of claim 1, wherein the inner diameter of the air bearing is defined to be greater than the length of the air bearing. The fan motor of claim 1, wherein the inner diameter of the air bearing is defined to be smaller than the inner diameter of the stator core surrounding the permanent magnet. The fan motor of claim 1, wherein a diameter of the first supporting part is defined to be larger than a diameter of the second supporting part. The fan motor of claim 1, wherein a diameter of the first supporting portion is defined to be larger than a diameter of the permanent magnet mounting portion. The fan motor of claim 1, wherein the impeller includes: a hub; and a plurality of blades protruding from an outer circumferential surface of the hub, wherein the hub is arranged to overlap with the air bearing in the axial direction to axially overlap the air bearing. Cover the air bearing. The fan motor according to claim 1, further comprising: a stator having a stator core and a stator coil. The stator core surrounds the permanent magnet and has an air gap with the permanent magnet. The stator coil surrounds the stator. an iron core; a first bearing receiving portion disposed between the impeller and the stator to accommodate the air bearing; a motor housing disposed on a downstream side of the first bearing receiving portion along the air flow direction to surround the The stator core; a fan hub, accommodated inside the shroud, one side of which surrounds the first bearing receiving portion, and the other side of which surrounds the motor housing; a plurality of fan blades, from one side of the fan hub An outer circumferential surface protrudes for mounting and coupling to an inner circumferential surface of the guard; and a second bearing receiving portion is received inside the motor housing to receive the ball bearing. The fan motor according to claim 9, further comprising: an external channel defined as an annular shape, and the external channel is located between the guard and the fan hub, so that a portion of the air sucked by the impeller passes from the suction port transmitted to the first discharge outlet; an internal channel provided inside the fan hub and the motor housing; and a plurality of communication holes provided in the fan hub to connect the external channel and the internal channel, So that another part of the air flows into the inner channel from an upstream side of the outer channel. The fan motor according to claim 10, further comprising: A plurality of first bridges extend from an upper end of the motor housing to the first bearing receiving portion to connect the first bearing receiving portion and the motor housing; a plurality of second bridges extend radially from the second An outer circumferential surface of the bearing receiving portion extends toward an inner circumferential surface of the motor housing to connect the motor housing and the second bearing receiving portion; and a plurality of second discharge ports are provided inside the motor housing. , to be connected with the internal channel and disposed between the plurality of second bridges to discharge air flowing along the internal channel. The fan motor of claim 11, wherein a plurality of fastening grooves are respectively provided in the plurality of second bridges, and a plurality of fastening holes are provided to radially engage with the plurality of fastening holes in the motor housing. The fastening grooves overlap, and the motor housing and the second bridges are coupled to each other through the fastening holes by a plurality of fastening members respectively fastened to the fastening grooves. The fan motor according to claim 11, further comprising: a plurality of fastening parts protruding radially from an outer circumferential surface of the motor housing toward an inner circumferential surface of the shield to fasten the shield and In the motor housing, a plurality of the first discharge ports are disposed between the plurality of fastening parts. The fan motor of claim 13, wherein the plurality of fastening portions and the plurality of second bridges are disposed radially on the outside and inside of the motor housing so as not to overlap with each other, and along the direction of the motor housing. A circumferential direction is alternately spaced apart from each other. The fan motor of claim 1, wherein the air bearing further includes: a sealing portion disposed to surround a portion of the rotating shaft, with a surface facing the rotating shaft at a predetermined distance from the rotating shaft. Spaced apart to form a gap through which air flow passes, and the sealing portion is arranged adjacent to the air bearing along the length direction of the rotating shaft to form a part of a flow path for air to enter and exit the gap, and is arranged to block the air bearing along the length of the rotating shaft. A portion of the air flows toward the gap from a circumference of the rotating shaft. The fan motor according to claim 15, further comprising: a housing portion provided with an internal space for accommodating the air bearing, wherein the sealing portion is arranged to extend radially from the housing portion toward the rotating shaft, one side of the sealing portion is fixed to the housing portion, and the other side is spaced apart from the rotating shaft by a predetermined distance, to form part of that flow path. The fan motor according to claim 16, wherein the sealing portion is disposed above the air bearing or below the air bearing along the length direction of the rotating shaft.

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